JP5105255B2 - Rotation body rotation control mechanism and door opening / closing device using the rotation body control mechanism - Google Patents

Description

The present invention relates to a rotation control mechanism for a rotator and an opening / closing device such as a door using the rotator control mechanism.
A rotation control mechanism for a rotary body that rotates around a joint such as a door or lid having a rotation axis, a reciprocating tool such as a bag, or a joint such as a finger or an arm, and that transmits force efficiently. provide.

In many of the embodiments shown in the drawings of the present application, when a door is opened, a force is stored in a spring (hereinafter referred to as an elastic body in which the support shafts at both ends return to their natural positions even if the spring is deformed). The present invention relates to “a technique for preventing a loud impact sound from being emitted when the door is closed” with respect to the door that is closed without permission. For this purpose, the present invention is made to "slowly rotate the door and seal it without generating intense impact noise". The technology that solves the problem of “slowly rotating the door and sealing without generating intense impact noise” deals with the door opening and closing device. The control mechanism is handled, and the means for solving this problem is a means for solving "the problems of other opening / closing devices not limited to doors".
That is, “a technique for preventing a loud impact sound when closed” is not limited to the conventional technology related to the opening / closing device similar to the lid and the bag, not limited to the door. This is also an effective means for solving the problem to be solved.

In order to explain “Technology to prevent loud impact noise when closed”, we explain what kind of phenomenon emits loud impact noise when closed, and how the present invention solves the problem Explain what to do. Based on this, the present invention will be compared with the prior art. In addition, specific examples of using the present invention in “industrial fields unrelated to doors” will be shown, and the background behind the technology of the present invention will be described.

Since the door pivot is vertical and the rotation of the door does not move up and down the center of gravity and there is no change in potential energy, a stationary door is “a force slightly above the maximum static friction force acting around the door pivot. To start spinning. The force required to rotate the door is very small.
Once it begins to rotate, the rotational resistance acting on the pivot of the door becomes a kinetic friction force that is less than the maximum static friction force, and its magnitude is drastically reduced. The door that started to rotate with the above-mentioned “slightly exceeding the maximum static frictional force” will work more than necessary, but air resistance will act on the door that has started to rotate, and the door will continue to rotate. For this purpose, it is necessary to apply a larger force than “the sum of the rotational resistance acting on the pivot of the door and the air resistance received by the door”.
When the force for rotating the door is approximately equal to the above-mentioned sum, the rotation of the door moves at a constant speed without acceleration. That is, the force for rotating the door is very small, and the door of the house equipment can be pulled and rotated by one natural rubber string having a diameter of about 1 mm even if it is a front door. A door that rotates with a very small force closes slowly without accelerating its rotational speed, and does not make a loud impact sound when closed.

Regardless of the position where the door is opened and released, the door closes arbitrarily, and in order to close slowly, a force that can barely start a stationary door works everywhere. It is necessary. That is, in all the ranges before the closing time in the rotation range of the door, the maximum static frictional force, or a size that is substantially equal to the above-mentioned sum of the kinetic frictional force and the air resistance received by the door, The force acting on the door is preferably constant regardless of the opening of the door.

In this way, when the force acting on the door is very small and the door moves at a constant speed without acceleration and closes slowly, when the latch attached to the side of the door comes into contact with the door frame, the latch will dent inside the door. It stops without stopping and the door is not sealed. In addition, when the door is closed with a strong force that causes the door to close, a loud impact sound is generated when the door is closed.
According to the present invention, “a door that rotates with a small rotational force rotates slowly, but there is no force to seal the door, it stops before it is sealed, and when the door is rotated with a force large enough to seal the door, , Generate a violent impact sound when closed. "
The door rotation range is divided into “range from fully open to just before closing (A)” and “range from just before to closing (Yes)”, and different forces are applied in each rotation range. It is what I did.

For example, in the embodiment shown in FIG. 1, the door is pulled by one pulling spring V to rotate the door. In FIG. 4, the spring mounting shaft Sj is the spring mounting shaft Sj in FIG. C is movably attached to the door, and the mounting shaft Sj is kept close to the door surface in the “(A) range” described above, and the mounting shaft Sj is the door in the “(A) range” described above. You can get away from the surface. The rotational force acting on the door is proportional to the distance Lv between the axis of the spring and the pivot axis O of the door, and is smaller in the “(A) range” and larger in the “(A) range”. There is a clear boundary between "(A) range" and "(I) range", and the magnitude of "force acting on the door" differs in each divided range.
The door of FIG. 4 has a “passage that continues from a position close to the door pivot axis O” where the force application point moves, and stops the force action point at a position close to the door pivot O “can be released”. ”And“ switching means ”for transferring the point of action of the force to a position far from the pivot axis O of the door.
When the “point of action of the force acting on the door” is at a position very close to the rotation axis, the force is transmitted very little, and when it is at a very far position, the force is transmitted very large.
“Releasable restraining means” is Gj1 for preventing the rotation of link A in the direction of arrow A in the figure, and “switching means” means that the rotation axis C of link A is at the predetermined opening of the door. Thus, the link A is rotated by traversing the axial center line Zv of the pulling spring V to move the force application point.
The magnitude of the force transmitted to the rotating body differs depending on whether the point of action of the force is at the start point or the end point of the passage. However, as will be described later, some of the switchgear according to the present invention have different device movements. Yes, it does not reciprocate one fixed movement. As a result, the movement of the door closing process and the door opening process are different.

The force that presses the door against the door and seals it is the magnitude that is added to the force that starts rotating the stationary door and the force that causes the latch to be recessed inside the door, and simply rotates the door. Greater than force.
In the present invention, the rotating body is rotated with a small force during the rotation, and is rotated with the above-mentioned large force only at the end of the rotation.
The length of the spring is minimal when the door is closed and the maximum force is required to seal the door despite the minimal spring force. The spring force starts at the maximum force required to seal the door, and the spring is stretched as the door is opened (if the spring that biases the door is a pull spring), the spring force increases as the door is opened. Become. Although the force of the spring that closes the fully opened door may be very small, the force of the spring increases.
The present invention prevents the increased spring force from acting on the door by controlling the force action line, and the spring force is applied in the vicinity of the door pivot O as shown in FIG. This allows the door to rotate with a small force despite the large spring force. This also means that the force to open the door is reduced in spite of the increased spring force when the door is opened, and the problem that the door feels heavy when the door is opened is solved.

However, “a loud impact sound when closing” is generated when the force acting on the door exceeds the force required for sealing, and the above-mentioned “force for indenting the latch inside the door is added to the force that starts rotating the door The extra working force that exceeds the “size” is converted into an impact sound.
Even if the door moves at a constant speed, the door accelerates as it rotates as long as the force continues to act on the door. A dynamic inertia force (hereinafter referred to as inertia force) is attached to the door that has reached the maximum speed just before closing. At the time of closing, the inertial force is added to “force for denting the latch inside the door to seal the door”. This inertial force is an extra force that acts as described above, and how to deal with it is a problem. The problem cannot be solved simply by taking a means that a different force acts in each divided range.

The inertial force attached to the door at the time of sealing is kinetic energy attached to the door, and is proportional to the square of the movement speed. Even if the speed of the door is small at the time of sealing, the inertial force is extremely increased, so that the acceleration of the door needs to be made as small as possible.
Even when the door moves at a constant speed without acceleration, the kinetic energy of the door is proportional to the weight of the door, and the inertia force attached to the door just before closing is large. Even if the speed just before the closing is small, the impact is large because it is a collision phenomenon in which the speed suddenly becomes zero when closing.
In this way, the inertial force that attaches to the door when sealed is very large even when the door speed is small. Accelerate the rotation speed. For this reason, it is desirable that the “(range)” to which a strong force is added is as small as possible, and if a strong force is applied only at the moment when the latch starts to be recessed, it can be sealed without acceleration. Also, when the latch begins to dent, the "force required to rotate the door" is drastically reduced, so the spring force is insulated from the door rotation, including the moment when the door hits the door. effective.

Apart from this, the "force required when the latch abuts against the door frame and seals the door" varies greatly depending on whether the door is moving or stopped. The “force required to seal the door” requires a much larger force when the door is stopped than when the door is moving.
In addition to this, the “force required when closing the door” is a force acting on the closed door, and is “force required when opening the closed door”. Therefore, if the “force required to seal the door” is small, the force required to open the closed door is small.

In summary, when the door is closed, the door is moving, not in a stopped state. For example, the “force required to seal the door” is reduced, and the force required to open the closed door is reduced.
In addition, the “impact of latching the inside of the door” mitigates the impact when it collides with the door stop.

The use of inertial force for sealing the door does not lead to sealing when the inertial force is insufficient, and directly connects to a large impact when working excessively.
The inertial force attached to the door increases when the door is largely opened and the hand is released, and decreases when the door is released after the door is released. In the former case, sealing is achieved, and in the latter case, it is not reached.
However, according to the present invention, when the door is sealed, a large force is applied only during the slight rotation of the door, and when the closed door is opened, the above-mentioned "while the door is slightly rotated". To prevent a large force from acting on the door, it feels as if the door is caught in something, and it is subject to great resistance.
In order to avoid such a situation, the present invention takes measures to prevent a large force from gradually acting while the door is greatly rotated when the door is closed.

As shown in FIG. 4, when the door is closed, the opening degree of the door is small when switching from “rotating means in the range (A)” to “rotating means in the range (I)”, and in the process of opening the door, The opening degree of the door is set large when switching from “rotating means in the range (ii)” to “rotating means in the range (a)”. Therefore, even if the dynamic inertia attached to the door in the process of closing the door is small and the position does not result in hermetic sealing, the opening degree of the “rotating means in the range of (i)” works in the process of opening the door. Sufficient force works to seal.
Since the “switching means” changes the form of the structure as the action point moves or the action line rotates, the state where the form of the “rotating means in the range (a)” changes to “(i) Since the form of the "rotating means in the range" is different, the movement of the device is different between the process of closing the door and the process of opening the door, so that the opening degree of the door that the "switching means" starts is different. become.

For example, in the embodiment of FIG. 72, the force of rotating the door by dispersing the spring force just before closing is insufficient, but the opening / closing device continues to move even if the door stops before closing. In addition, even if the "force acting on the door" does not cause the door to rotate without the force to rotate the door, the opening and closing device continues to move and the force to rotate the door grows into a force that seals the door and seals the door Will do.
In addition, measures are taken to prevent the spring force from being transmitted to the door by bringing the closing device into contact with the door frame in front of the door and separating it from the door before stopping, so that the spring force is not transmitted to the door. If the form changes, the opening degree of the door that the “switching means” starts becomes different between the process of closing the door and the process of opening the door, and decelerates when opening the door. It does not stop at the position where the means is activated. No matter where you take your hand off the door, the door will not stay stationary.

By taking such measures, the door can be opened without resistance when the door is opened, even though a strong force is applied only when the door is sealed, and the spring force is applied to the door if the dynamic inertia is not attached. Even if it is set to “a small force that cannot be sealed,” the door will always be sealed.
In the embodiment of FIG. 4, the opening degree of the door when the link A rotates greatly when the door is closed, and the opening degree of the door when the link A greatly rotated when the door is opened returns to the original position. In contrast, the range of strong force acting when opening the door is wider than the size of “(range)” where a strong force acts when the door closes. Even if the “(range)” where a weak force is applied when the door is closed, the “(range)” where a strong force is applied when the door is opened.
This means that even if the door is sealed due to inertial force, if the hand is released from the door in a slightly opened position, a strong force acts on the door even if the inertial force is not attached to the door. Therefore, the door does not remain stopped but is sealed.
In other words, when the door is opened at a slightly opened position, the opening of the “(range) rotation means” works, and if the force is sufficient to seal the door, the door is closed. Thus, even if the opening is at a position where the “rotating means in the range (A)” works and does not have the force to seal the door, it is always switched to the “rotating means in the range (I)” at the time of sealing.

The fact that the door stops at a slightly open position is also a function that can accommodate outpatients with the entrance door half-opened, but the door does not remain stopped no matter what happens The means to do so is a function that does not remain stopped even if the door is temporarily stopped just before closing.
In a position where the door is slightly open and within the range of “(A)” in the process of closing the door, there is no “force to rotate the door” in the spring, and the door continues to rotate with dynamic inertia. Even if the door rotation is braked and the door is stopped, or the spring force is not transmitted to the door, the door rotation means continues to operate and switches to "rotating means in the range (ii)". It comes to sealing.
The "(A) range" where the brake was applied in the process of closing the door is a state where the inertia force is not attached to the door in the process of opening the door, but the "(A) range" where the spring works strongly. When the door is opened, if the user releases his / her hand in the “range of opening the door”, the door does not remain stopped but is sealed. Further, it is natural that the sealing is achieved when the rotation means is further opened to the range of “(A) range of rotating means”.
When the door closes, the “spring range when opening the door” may be set so that the spring force is insufficient to rotate the door and rotate with inertial force, or a brake is applied with resistance. Even if it rotates, the door will always be sealed when the door is opened and released, and it will not stop halfway.

In the present invention, by setting the rotation speed of the door at the time of sealing in this way, the magnitude of the inertial force attached at the time of sealing can be made a predetermined size, and the inertial force attached to the door works without excess or deficiency. Is sealed. As a result, the impact noise is reduced, and the force required to open a closed door is reduced.
That is, since the inertial force attached to the door is greatly involved in the work of sealing the door, the impact sound is reduced and the force required to open the closed door is reduced.

It is very difficult to adjust the force acting on the door so that it does not generate an impact sound when it is closed, and it is very difficult for one door. Since the force required for sealing varies from door to door, it is difficult to provide a door closer that slowly rotates and quietly closes to any door.
“Door closers with hydraulic cylinders” are commonly used, and are designed to increase the strength of the springs required to seal the doors and increase the strength of the springs. When closing, the spring does not expand and contract instantly due to the viscous resistance of the oil, but the door rotates slowly and closes gently.
Also, when the door is sealed, a large force of the spring is applied by removing the force or resistance in the opposite direction.

The inertial force that attaches to the door when it is sealed is very large even when the door speed is low, and a very large force is required to brake the door.
The “door closer with a hydraulic cylinder” employs viscous resistance of oil as a means to counter this large inertia force, and exerts a large force on the opposite side of the door closing direction. The force of the spring attached to the “door closer with a hydraulic cylinder” is simply the magnitude of the inertia force attached to the door added to the magnitude of the force that rotates the door. It becomes the size.
On the other hand, in the present invention, the door rotates without acceleration in the “(range)”, and the above-described deceleration is performed at the end of the “(range)” or the beginning of the “(range)”. By taking measures, the rotational speed at the time of closing is adjusted. The speed reduction means described above does not cause a problem if the rotation means continues to operate even if the rotation of the door stops. Therefore, the speed reduction means does not increase the spring force as in the case of a “door closer with a hydraulic cylinder”. In addition, the present invention removes “resistance acting in the opposite direction to the spring force” such as oil resistance, friction resistance or gear rotation resistance, and efficiently transmits the spring force to the door without friction. The power of is very small.
The spring used in the opening / closing apparatus of the present invention can be expanded and contracted by the force of the fingertips, as in the rubber string described above, but the spring used in the “door closer with a hydraulic cylinder” only contracts over the entire weight. A spring of extraordinary strength is used.

In the “door closer with a hydraulic cylinder”, the viscous resistance of the oil applies a force in the direction opposite to the spring force in the range of rotation of the door until just before closing, and the “door closer with a hydraulic cylinder” By reducing this, a small force is applied to the door. Normally, the device that transmits the force removes the resistance as much as possible and converts the force into work efficiently, but the door closer equipped with a hydraulic cylinder bothered the resistance to the door that rotates without resistance, and the spring force is inefficient. This is a unique technique as a technique used in a device for transmitting a normal force.
In contrast, the present invention actively improves the rotation transmission efficiency by using a bearing or the like. By not using friction, the operation is stabilized and the deterioration of performance due to wear is reduced.

In the "door closer with a hydraulic cylinder", the spring force when the door is closed and rotated is greater than the resistance that overcomes the resistance and rotates the door, and the inertia that attaches to the door by acceleration of the door and by weight It is bigger than force. The present invention closes with a small force so as not to accelerate as much as possible so that the inertial force does not increase, and the strength of the spring of the “door closer with a hydraulic cylinder” is larger than the above inertial force. On the other hand, the strength of the spring of the present invention is a force that is simply greater than the force that rotates the door.
As described above, the “door closer having a hydraulic cylinder” needs to store a force larger than the force of simply rotating the door when the door is opened, and has a drawback that the door feels heavy. It was necessary to push and open a heavy door simply by attaching a function to close it.

If the sealing force is reduced even in the “door closer equipped with a hydraulic cylinder”, the force when opening the closed door is small and the door does not feel heavy, but the force acting on the door when opening further is oil. This is the power to overcome the resistance and close the door. A door that closes with a large force requires a large force when opened, but a door that rotates with a small force does not require a large force when opened, even if the spring force is strong as in the present invention.
The force required to open the door is the force acting on the door regardless of the spring force. In the present invention, when the door is closed, resistance such as “a force opposite to the closing direction” such as resistance is not applied, so that an extra force corresponding to the resistance of the oil is required as compared with the case of the “door closer having a hydraulic cylinder”. Absent.

A door closer with a hydraulic cylinder closes slowly and is an excellent product with low impact noise when closed, but it is expensive due to oil leakage problems. Many inventions including the above-mentioned prior art try to obtain equivalent performance by means of replacing hydraulic cylinders, but as in the present invention, the door until just before closing is `` stopped, There is no “rotating means in the range of (A)” characterized in that it is kept in a “rotating state with a weak force that does not stray”.
For this reason, many inventions address the problem of how to decelerate a door that has been greatly accelerated at the time of closing, and employ braking means and buffering means as means for solving the problem. In many cases, frictional resistance is applied, and braking means and buffering means are added. As in the present invention, “means for controlling the direction in which the force acts” is not taken into the operation of the switchgear.
The present invention has been made to eliminate the disadvantage that the door feels heavy when the door of the door closer provided with the hydraulic cylinder is opened, and to provide a door closer having performance equal to or higher than that of the door closer provided with the hydraulic cylinder. It is what.

Many door closers, including “door closers with hydraulic cylinders,” employ “door rotation speed reduction means” that resist the operation of the device to solve the problem of reducing the “shocking noise when closing”. ing.
Patent Document 2 uses a linear movement of a gear moving along a rack as a biasing means of the door, and the speed of the door is reduced by a load generated at that time when the rack and the gear are engaged. In industrial fields other than doors, many means for controlling the rotational speed or torque are used via a reduction gear and a switching device. However, as the speed decreases, the rotational resistance of the gear increases.
The present application does not control the magnitude or rotational speed of the rotational force with a gear. Patent Document 2 is different from the present application in that a constant load is applied when the gear rotates.
Patent Document 3 is a closed door cushioning mechanism that has a spring that often acts as a force against a spring that biases the rotating body in the closing direction, but applying a restraining force in the direction opposite to the closing direction is simply a force in the closing direction. Is just reduced.
In the present application, even if a force acting in the direction in which the rotating body rotates is added or removed, a resistance or other “force for reducing the force for energizing the rotating body” is not newly added. In this application, the force is transmitted to the rotating body without resistance, and the magnitude of the rotating force is changed by controlling the “distance between the action line and the rotating shaft to the force acting around the rotating shaft”. When the magnitude of the rotational force changes, there is little or no rotation of the rotating body.

Whether it is the viscous resistance of the oil or the frictional resistance of the gears of the “door closer with a hydraulic cylinder”, if viewed from the door, if the force transmitted to the door is the same, it may be reduced by the resistance but in the opposite direction Regardless of what is reduced by the spring, it does not matter what "means to reduce" is. In the case of a door, even if the internal resistance of the door closer increases, the rotational resistance of the pivot axis O of the door does not increase. Regardless of whether the door closer is provided with a cylinder or in the above-mentioned patent document, all of these door closers reduce the force by applying a large resistance to the force of a large spring, and merely transmit a weak force.
The means for rotating the door while resisting such a large force overcomes this resistance and rotates the door. Therefore, when the door is opened, the spring force is increased more than necessary. I make it feel heavy.

Since the door must be sealed with a large force at the end of rotation, the spring force is set to a large value. As a result, the door rotates at high speed, and many door closers employ resistance as a speed reduction means.
According to the present invention, even if the resistance is not applied, even if the force of the spring is large, the door is acted small, and an excessive force is not provided to the door.
In other words, “the force acting on the door before the door closes” is a small force that rotates the door, and “the force acting on the door when the door is closed” is used to dent the above latch inside the door. This is a large force that distinguishes the rotation range of the door and applies the necessary and sufficient force to the door in the distinguished rotation range so as not to supply more energy than necessary to the door. The sound is reduced. That is, the door rotation range is divided into two before and after closing, and forces of different magnitudes are applied in each range.
That is, in an opening / closing device in which a rotating body rotates by a force acting around a rotating shaft, the rotating force acting on the rotating body is kept small, and the rotating force in the range (A) is greatly affected. An opening / closing device comprising a "rotating means in the range of (ii)" and a "switching means" for switching the rotational force from small to large or from large to small. The opening / closing device is characterized in that the magnitude of the rotational force or the magnitude of the force acting on the rotating body changes as the “distance between the rotating shaft and the line of action of the force” changes.
This switchgear has a clear boundary between the two rotation ranges where forces of different magnitudes work, and automatically switches from strong to weak or from weak to strong. There is a feature that suddenly changes.

In the present invention, the force is efficiently converted into a rotating body in an environment where resistance is removed as much as possible, and the "distance between the action line of the force acting around the rotating shaft and the rotating shaft" is controlled. Therefore, the rotational friction resistance around the pivot axis O of the door is only an element that deteriorates the transmission efficiency, and the transmission efficiency is better than that of the above rotation transmission means. The result is improved technology.
The present invention processes mechanically without using a “means for reducing the force for energizing the door with resistance”, and applies a force in the direction opposite to the rotational direction, such as resistance, like a door closer. It can transmit the rotational force efficiently without using a means to reduce the force and a means with a loss of energy like a reduction gear by a gear mechanism. It is intended to prevent it from being felt heavy when the door is opened.

The present invention is an efficient means that does not involve friction, and can reduce the speed reduction device and the switching device from the rotation devices in the industrial field other than the door, thereby simplifying the device.
The means for changing the magnitude of the force by controlling the “distance between the acting line of the force acting around the rotating shaft and the rotating shaft” of the present invention can be particularly effective when used for a door. It can eliminate the “flaws that feel heavy when opening the door”. Needless to say, the technology for solving this problem can be used in industrial fields other than doors.

The “means for making the magnitude of the force acting in the distinguished rotational range different” of the present invention will be described.
In the opening / closing device in which the force F acts around the rotation axis and the rotation body rotates, there is M between the rotation force M acting on the rotation body and the distance L between the rotation axis and the line of action of the force. = F × L The relational expression holds, and when the force F acting around the rotation axis is the same, the smaller the distance L between the rotation axis and the line of action of the force, the smaller the rotation force M acting on the rotating body. Becomes smaller and larger the larger.
Speaking of the door, the door does not move easily even if the vicinity of the pivot of the door is pushed with a strong force, and the door rotates with a small force when pushed near the handle.
For example, as shown in FIG. 1, in a door D that rotates by connecting a connecting shaft C provided on the door D and a fixed support shaft Sw provided on the door frame W by a pulling spring V, the position where the spring attaches to the door is the door. The closer to the pivot axis O, the smaller the “distance between the rotating shaft and the line of action of the force” and the smaller the rotating force acting on the rotating body, and the smaller the force acting on the door even if the spring force is large.

The switchgear shown in FIG.
A rotating body that rotates about the axis of the rotating shaft; a fixing portion that fixes the rotating shaft; a spring that connects a connecting shaft provided on the rotating body and a fixed support shaft provided on the fixing portion; In the rotating opening / closing device, either the connection shaft or the fixed support shaft, which is closer to the rotation shaft, is movably attached, and moved from a position near the rotation shaft to a position far from the rotation shaft. An opening / closing device that increases the distance L between the line of action of the force and the force.
In FIG. 4, “the fulcrum of the spring that is attached to the door or the door frame (hereinafter, the door frame refers to the door frame or its surrounding wall surface) and is closer to the pivot of the door” is the connection axis C or the door frame provided on the door. The movable support shaft Sj is provided at the tip of the link A that is rotatably supported around the fixed support shaft Sw provided, and the movable support shaft Sj and the spring are centered on the pivot axis O of the door as the door rotates. However, when the spring crosses the position of the connecting shaft C or the fixed support shaft Sw, which is the rotation shaft of the link A, the direction in which the spring rotates and urges the link A changes, and the contact comes into contact. The stationary link A rotates, and the moving support shaft Sj moves to a position far from the position close to the pivot axis of the door just before the door is closed. The “distance Lv between the rotating shaft and the force action line” is increased, the rotational force acting on the rotating body is large, and the force acting on the door is large even if the spring force is small.
The distance L between the rotating shaft and the line of action of the force slightly changes in the “(A) range”, and the rotational force acting on the door slightly changes. The magnitude is clearly different from the rotational force acting on the.

The switchgear shown in FIG.
4 is an opening / closing device having the same structure and operation as that of FIG. 4, but also a structure including a single spring rotating device shown in FIG. 1 and a “sealing device in which a cam wheel presses a sliding surface”. As in the case of FIG. 4, when the tension spring V crosses the rotation axis Q of the rotating body J, it switches from “rotating means in the range (A)” to “rotating means in the range (I)”. Since the body J is connected not by a link but by a pulling spring V as shown in FIG. 12, the rotation of the closing device and the rotation of the door are not linked, and the rotation of the device continues even if the rotation of the door stops. In the case of FIG. 12, the rotation of the apparatus continues even if the rotation of the door is stopped as in the case where the link A and the rotating body J are movably connected to be connected by a spring.

In FIG. 15, one fulcrum C of the spring is attached to the door and the other Sj is attached to the door frame. Becomes smaller.
In FIG. 16, one fulcrum Sw of the spring is attached to the door frame and the other sj is attached to the door. Becomes smaller.
As shown in FIG. 6, when the rotating body J is rotated by pulling the supporting shaft Sa provided at the tip of the rotating body J with a spring, the supporting shaft Sd that is not attached to the rotating body with the supporting shaft is attached to the spring. If the spring is extended and retracted in the tangential direction of the support shaft Sa circular movement at a position far from O, the expansion and contraction of the spring is large. The expansion and contraction of the spring becomes smaller when it expands and contracts in the radial direction.
If one of the spring spindles is fixed and the other moves,
When the direction of the spring is the direction of movement of the support shaft, it is large, and when the direction is perpendicular to the direction of movement, the expansion and contraction of the spring is small. The expansion and contraction of the spring is small as it moves perpendicular to the moving direction of the support shaft of the spring.
The spring for rotating the rotating body is attached in the radial direction of rotation of the rotating body, so that the spring expands and contracts, the force of the spring works strongly in the radial direction and weakly in the circumferential direction, and the force involved in the rotation becomes small.

When the tension spring V is attached to the door or the rotating body J in this way, the expansion and contraction of the spring and the change in the spring force are small, and the decrease in the strain energy of the spring is also small. As a result, the acceleration of the door is also reduced.
“Rotating means in the range (A)” keeps the point of action of the force in the vicinity of the pivot of the door, and as shown in FIGS. " By attaching one spring as described above, the spring acts in the “(A) range” no matter how large the force of the spring is, and acceleration is also reduced.
Since the acceleration of the door is not due to the strength of the spring, but due to the amount of change in the strain energy of the spring due to the amount of expansion and contraction of the spring, even if the force of the spring is large, the door is kept at the center of rotation. The force to rotate is weak, and even if the door is large, the movement of the device is small, so there is little expansion and contraction and little acceleration.
Even if the spring force is increased in the “(A) range”, the door does not rotate unless the spring length changes, but if the change is small, the acceleration is small. In the range where the force acting on the door is small, in the “door closer with a hydraulic cylinder”, the air resistance slows the rotation of the door in the closing rotation of the door, as the viscous resistance of the oil slows the expansion and contraction of the spring. Air resistance works in the same way as oil viscosity resistance.

The present invention seals the door with as little force as possible. Just before closing, the door rotation speed is braked, or the operating line of force F passes through the vicinity of the door pivot O so that the force is insufficient and the rotation resistance around the door pivot O is increased. However, even if it is necessary to increase the "sealing force of the door", or even if the door is in a state of stopping just before closing, the device can be operated even if the force to rotate the door is small. Therefore, it is necessary to make the spring force as small as possible so that the above operation continues, and so as not to accelerate due to a strong force acting just before closing.

The sealing device of the present invention including the sealing device of FIGS. 15 and 16 applies a strong force to the door even if the spring force is weak, and a cam wheel is attached to the tip as in the sealing device of FIGS. The cam wheel rotating body rotates, and the cam wheel is sealed by a so-called wedge effect in which the cam wheel moves simultaneously along the sliding surfaces attached to the door and the door frame as shown in FIG. In both the former and the latter, the movement of the cam wheel is on a passage along the “closed door surface”, and the cam wheel moves substantially in parallel with the closed door surface to move the “sliding surface substantially parallel to the closed door surface”. It is pressed and exerts a large sealing force substantially perpendicular to the closed door surface.

The former is supported by the rotating shaft of the cam wheel rotating body fixed via the cam wheel rotating body, and the latter is supported by the door frame W via the sliding surface of either the door or the door frame. Supported by In either case, the sealing force is supported by a rigid portion that does not deform, and the elastic body of the urging means does not oppose. Since the urging means acts in the circumferential direction which has nothing to do with the support of the sealing force, a small force is sufficient. This simple reason is a feature of the present application, and is an effective means for driving with a small force while supporting a large force in an opening / closing body other than a door, as will be described later.

A large sealing force is established due to the presence of a reaction force, and the structure of the device is not a movable structurally mechanically unstable state but a statically balanced state in which the device framework does not move. The reaction force of the sealing force increases as the device does not move, which means that it does not open when opening a closed door. The more tightly sealed with a weak force, the more the weak force resists even if it tries to open with a strong force.
For example, except for the case where the force of the spring acts directly on the door at the time of sealing as in the embodiment of FIG. 4, the force Fb that the wheel presses the sliding surface as shown in FIG. 6 is used as the sealing force. It is desirable that the force for sealing the door works at right angles to the closed door. In FIG. 6, when the line of action of the force Fb and the axial center line Za of the link A are at right angles to the closed door, the sealing force becomes maximum. . However, in this case, the closed door cannot be opened unless the line of action of the force Fb and the axial center line Za of the link A do not overlap with each other.

In this way, the device that only has one spring attached to the sealing device that functions only in the “range from just before closing to the closing time (i)” seems to rotate with a weak force and a large force acts at the end of the rotation. become. In addition, since the rotation operation is limited to the vicinity of the door pivot O and the sealing operation is limited to the vicinity of the door frame, the apparatus of the present invention is parallel to the closed door surface and is elongated along the door frame. Not accommodated in a flat case.

For example, the sealing device shown in FIG. 19 is inherited from the “rotating means in the range (A)” as in the sealing devices in FIGS. Since the “means” is insulated from the rotation of the door, the operation continues even if the rotation of the door stops as shown in FIGS. However, when it is inherited, there is no need to rotate the door, so the spring expands and contracts in an instant in an unloaded state, and without any intermission, the "rotating means in the range (A)" to the "(A) range Switching to “rotating means”, and the door continues to rotate, so that it is sealed without being decelerated. Therefore, the “switching means” requires a delay mechanism.

In FIGS. 47 and 48, a delay mechanism is directly incorporated in this "switching means", and a one-way operation damper is incorporated. As means for replacing the one-way operation damper, “means for insufficient force” is generally taken. In FIGS. 3 and 4 and FIGS. 28 to 33, the spring for biasing the rotating body is the rotating body at the beginning of the “switching means”. In the vicinity of the rotation axis, the “switching means” moves away from the rotation axis. Although the spring force is strong at the beginning of the “switching means”, the sealing force gradually increases as the “switching means” proceeds.
In FIG. 13, the force of the spring is applied in the direction in which the door opens, but the load is applied. The spring force is applied in the direction in which the door opens so that it does not open.
112 and 113, the gradient of the sliding surface K on which the wheel B moves becomes proportional to the magnitude of the inertial force attached to the door, and is delayed by means for changing the inertial force to a braking force. 112 and 113 are excellent in that they do not open the door when the elastic spring returns, although the spring expands and contracts by the force in the direction of closing the door.
Any of the means for decelerating with these “means for lack of force” is a means to replace “deceleration with one-way operation damper”, but the same effect as “deceleration with one-way operation damper” cannot be obtained. Absent.

The opening / closing device shown in FIG. 19 includes a rotating body that rotates about the axis of the rotating shaft, a rotating device that applies a force near the rotating shaft, and a sealing device that applies a force to a distant position. A device relayed to the device, the switching device having a "switching means" in which the point of action of the force acting on the rotating body moves to switch from small to large or from large to small,
In FIG. 19, a rotating device Bf, Wf in which a force acts near the door pivot O and a sealing device Bb, Wb in which a force acts at a position far from the door pivot O to seal the door D are provided. The device is relayed from the rotating device to the sealing device, and the point of action of the force acting on the door is the position Wf close to the pivot axis of the door, “the rotating means in the range (A)” and the far position Wb. “Rotating means in the range of (i)” and “switching means” that moves from a position close to the pivot axis of the door just before the door closes. With respect to the door, the rotational force is switched from small to large in the closed rotation, and from large to small in the open rotation.

The opening / closing device of the present invention handles a rotating operation in which a force acts near the door pivot O and a sealing operation in which a force acts far from the door pivot O. One device as shown in FIG. Are processed, and two are processed as shown in FIG.
In FIG. 19, the operation involved in the rotation is limited to a small circle around the pivot O so that the wheel Bf of the rotating device revolves around the pivot O while making contact with the sliding surface Wf provided in the vicinity of the pivot O. . Further, after the wheel Bb of the sealing device moves on a large circular orbit centered on the pivot O, the operation for sealing is performed so that the sliding surface Wb provided at a position far from the pivot O is pressed. The wheel Bf of the rotating device can continue to be engaged with the door or the door, but the wheel Bb of the sealing device is disengaged. The operations of the rotating device and the sealing device are limited to a range that is long in the direction parallel to the door surface closed along the door frame and short in the perpendicular direction, and can be stored in the elongated case.
21 and 72 show that the wheel Bf of the rotation device is engaged and disengaged so that the wheel Bb of the sealing device continues to be engaged with the door or the door. The wheel Bb involved in the rotation is limited to a small circle around the cam wheel rotating body rotation axis C, and extends “on a track away from the axis O”. FIG. 49 shows a “trajectory moving away from the pivot axis O” along the door frame. In this case as well, the rotating device and the sealing device can be housed in an elongated case.

Also, for example, the opening / closing device shown in FIG.
A rotating device in which a force is applied around a pair of rotating shafts so that two rotating members separated from each other rotate relatively, and the cam wheel rotating member Jq rotating about the cam wheel rotating member rotating shaft Qj is a cam member. A cam body KK that rotates about the rotation shaft Qk is provided, and the sliding surface K provided on the cam body KK presses the cam wheel B that is mounted on the tip of the cam wheel rotation body Jq to rotate the cam wheel rotation body Jq. A rotating device,
When the cam wheel B is in the middle of the sliding surface K, the distance between the line of action T of the force by which the sliding surface K presses the cam wheel B and the cam wheel rotating body rotation axis Qj is small. The "rotating means in the range of (A)" and the cam wheel B rotate at the end of the sliding surface K so that the force action line T rotates and the force action line T and the cam wheel rotating body. The opening / closing device includes a “rotating means in the range (ii)” in which the distance to the rotation axis Qj is largely switched.
In FIG. 81 (a), the sliding surface K presses the wheel B and the cam wheel rotating body Jq rotates. In FIG. 81 (b), the sliding surface K presses the wheel B and the cam opening rotary shaft C Revolve. The two rotating bodies that are separated from each other are relatively rotating.
The rotational force for rotating the cam wheel rotating body Jq increases as the line of action T of the force with which the sliding surface K presses the cam wheel B becomes farther from the cam wheel rotating body rotation axis Qj.

As described above, the closer the force action point is to the center of rotation, the smaller the force acting on the rotating body, and when the force action point is the center of rotation, the force acting on the rotating body is zero. By moving as close as possible to the center of rotation, the force acting on the rotating body approaches zero.
In the embodiments of FIGS. 1, 4, 19, and 35 described above, the door is rotated in the “range (a) from when fully open until just before closing” by making the force acting on the rotating body as close to zero as possible. The ratio of the magnitude of the force to force and the force that seals the door in the “(range) from just before closing to the closing time” approaches infinity, and the point of action of the force is limited to “(range)” By moving closer to the center of rotation without changing the strength of the spring, it is possible to obtain the force to seal the door in the “(range)”. As a result, it is not necessary to keep the force application point away from the center of rotation in the “range (ii)”, and the apparatus can be designed to be small.

Further, in the relational expression M = F × L, when the rotational force M acting around the rotation axis is the same, the force acting on the rotating body as the distance L between the rotation axis and the line of action of the force becomes smaller. F increases and decreases as the value increases.
For example, the switchgear shown in FIG.
An opening / closing device comprising a rotating body J that rotates about an axis of a rotating shaft C, and an opening / closing body D that rotates by the rotation of the rotating body J, wherein the rotating body J is a support shaft that is far from the rotating shaft C. “Rotating means in the range of (A)” has a supporting shaft Ia located close to Bf, and rotates the opening / closing body D by a small force acting on the supporting shaft Bf that balances the rotational force acting around the rotating shaft C. And a "rotating means in the range of (ii)" that rotates the opening / closing body D by a large force acting on the support shaft Ia that balances the rotational force acting around the rotation axis C, and acts on the opening / closing body D An opening / closing device having a “switching means” for switching the force from small to large or from large to small,
In FIG. 21, for the rotating body J that rotates around the connecting axis C by rotating force, the force that the wheel B located at the position away from the center of rotation C presses the sliding surface Kf is weak, and from the center of rotation C. The force with which the support shaft Ia at the close position pushes the link A is large.

As shown in FIG.
A rotating device in which a force is applied around a pair of rotating shafts so that two rotating members separated from each other rotate relatively, and one rotating member rotating around one rotating shaft is far from the vicinity of the rotating shaft. The other rotating body rotating around the other rotating shaft C has a wheel B mounted on a support shaft Ib provided at the tip, and the wheel B and the sliding surface K are In an opening and closing device that moves relative to each other by applying a pressing force Fb to each other,
The intersection angle Θf between the axis line Za of the other rotating body passing through the other rotating shaft C and the supporting shaft Ib and the line of action of the pressing force Fb is large, and the line of action of the pressing force Fb and the other rotating shaft When the distance to C is large, the pressing force Fb balanced with the rotational force M acting around the other rotation axis C is small, the crossing angle Θf is small, and the line of action of the pressing force Fb and the other When the distance from the rotation axis C is small, the pressing force Fb that balances the rotational force M increases.
In FIG. 6, the sliding surface K is fixed and the rotation axis C of the link A revolves. In FIG. 57, the rotation axis of the link A is fixed and the sliding surface K revolves. Two rotating bodies separated from each other rotate relatively.

FIG. 6 shows a case where the one rotating body having the sliding surface K of the opening / closing device is fixed to the fixing portion W and the rotating shaft C 1 of the other rotating body on which the wheel B is mounted revolves. "Rotating means in the range of (A)" where the force acting on the door is small and the position where the wheel B is far from the door pivot O of the sliding surface K. The wheel B moves along the sliding surface K with a predetermined opening degree of the door as a boundary, and “the action of the force”. “Switching means” for switching the distance Lf ”between the line F and the center of rotation from small to large or from large to small. The crossing angle Θf between the axis A of the link A and the line of action of the pressing force Fb changes as the door rotates, and the wheel B slides in a direction in which the crossing angle Θf is an obtuse angle when it is at a right angle. It moves along the moving surface K.

Similarly, the switchgear shown in FIGS.
The connection shaft C provided on the door D and the fixed support shaft Sw provided on the door frame W are connected by two links J and A. The door D, the door frame W and the two links J and A are constituted by four links. The link device is a rotation mechanism that transmits the rotational force around the rotation axis of one of the two links J and A to the door D, and the crossing angle Θaj between the axis lines of the two links J and A is zero. Alternatively, the “rotating means in the range (A)” in which the rotational force is transmitted in a range that does not approximate 180 degrees, and the rotational force in the range in which the crossing angle Θaj approximates to zero or 180 degrees is transmitted (“I”). An opening / closing apparatus comprising a "range rotating means" and a "switching means" characterized in that the crossing angle Θaj rotates greatly with a slight rotation of the door D.
61 and 63, the rotational force M acting around the center of rotation C of the rotating body J balances with the moment due to the axial force F acting in the axial direction of the link A, and the link A presses the tip C of the rotating body J. In the state where the axial center line Zj of the rotating body J overlaps with or is aligned with the axial center line Za of the link A, the distance F between the acting line of the axial force F and the center of rotation C is small and the rotational force M is the force F. The distance Lc between the line of action of the axial force F and the center of rotation C increases as the crossing angle Θaj between the axial line Zj of the rotating body J and the axial line Za of the link A increases. The rotational force M is converted into a small axial force F.
The opening / closing device shown in FIG. 61 is in a state where the intersection angle Θaj approximates to zero at the end of the rotation of the door and the axis of the rotating body J and the link A overlap, and the opening / closing device shown in FIG. In the state where the axis cores of the rotating body J and the link A are in a straight line, both are arranged on a straight line, and the rotational force M is greatly evaluated as the axial force F.

Further, for example, the switchgear shown in FIG.
The connecting shaft C provided on the door D and the fixed support shaft Sw provided on the door frame W are connected by three links J, A, AA. The door D, the door frame W, and the three links J, A, AA 5 An opening / closing mechanism that transmits the rotation of the rotating body J that rotates about the fixed support shaft Sw to the door D that rotates about the pivot O of the door.
The above-mentioned two links A and AA are kept in a straight line, and the connecting shaft P of the rotating body J and the link A pulls the door) “Rotating means in the range of (A)” and the two links A and AA are bent. “Rotating means in the range of (ii)” in which the connecting shaft PP of the two links A and A pulls the door, and “switching means” door in which the rotating body J is relatively separated from or integrated with the link A. Opening and closing mechanism provided.
The distance rp between the center of rotation Sw of the rotating body J and the line of action of the traction force acting on the connecting shaft P is greater than the distance rpp between the line of action of the traction force acting on the connecting shaft PP and the rotation acting on the center of rotation Sw of the rotating body J. The force is weak when the connecting shaft P having a large turning radius pulls the door, and strong when the connecting shaft PP having a small turning radius pulls the door. The “switching means” works when the rotating body J and the link A are relatively integrated, but the force acting on the door does not change gradually, but the “switching means” suddenly works. There is a feature.

For example, the opening / closing device shown in FIG.
A passage K1 continuous from the vicinity of the door pivot O provided on the door, a passage K3 and a wheel B3 continuous from the vicinity of the door pivot O provided on the door frame, and a wheel B1 and a wheel B3 at both ends. And a link A provided with a sliding surface K2 in the middle portion, substantially the same as the door surface where the link A is closed while the wheel B1 moves along the passage K1 and the wheel B3 moves along the passage K3. By moving along the door frame in parallel, the wheel B2 comes into contact with the passage K2 and moves along it before the closing, so that the wheel B1 becomes the action point, the wheel B2 becomes the fulcrum, and the wheel B3 becomes the force point. The link A functions as a switchgear.

In the embodiment of FIG. 81, the lever acts immediately before closing, but in FIG. 60, the wheel B1 stays in the vicinity of the door pivot O in FIG. The wheel B moves relatively along the sliding surface K and approaches the center of rotation Sw or C of the sliding surface K as it closes. However, as in the case of FIG. 35, even if the wheel B moves in “range (A)”, the “action line Fb of the force by which the wheel B presses the sliding surface K” remains near the pivot axis O of the door. Even if the wheel B does not move in the “range (ii)”, the “action line Fb of the force that the wheel B presses the sliding surface K” rotates and moves far away from the pivot axis O of the door. The sliding surface K slightly rotates in the “(range)” and rotates largely in the “(range)” to function as a lever.

The switchgear shown in FIGS. 6, 13, 21, 56, 60, and 81 is similar to the switchgear shown in FIGS. 3, 4, 15, 19, and 35, by changing the distance between the center of rotation and the line of action of force. The force acting on the door is changed, and the rotational force M acting at the center of rotation is converted into a “small rotating force F that rotates the door” and “a rotating means in the range (A)” and converted into a large force F. Thus, a “rotating means in the range of (ii)” for rotating the door is provided.
All of the above-described embodiments are rotation control mechanisms in which the “forces acting on the rotating body” F and M change in proportion to or in inverse proportion to the magnitude of L according to the relational expression M = F × L described above. Thus, it includes “rotating means in the range of (A) and (I)” and “switching means”.
The following is a “conventional technique in which a large force is applied at the end of rotation” and is compared with the present application.

Even in industrial fields other than doors, there are many "opening and closing devices where a large force acts at the end of rotation", and work is done so that the working force differs between the state where the door is rotating and the state where it is sealed and stationary. The force that works in the previous and previous movements is different.
For example, a robot arm has different working forces in a range from picking an object to a range from picking to lifting. The working force differs when the laundry basket is opened and when it is stationary with the laundry in between. Whether cutting or grabbing, the tools and machines that perform these tasks are generally reciprocating. The blades move up and down like a press machine, There are blades that share a rotation axis and open and close relatively.
The present invention does not divert the technologies employed in these switchgears, and is not merely a modification of these technologies at the design stage. Therefore, the present invention has an effect on these switchgears, and suggests improvement of these switchgears.

Patent Document 1 relates to an electric door that makes the magnitude of the rotational force different from the middle and the last of the rotation. Although there is no specific description of the control method, the magnitude of the rotational force is mechanistically as in the present application. It is managed by electrical signals rather than being processed.
In Patent Document 1, the magnitude of the rotational force is not controlled by an associated link mechanism but is managed by an electrical signal. The control means for the rotational force supplied to the rotating body is different from the present application.
Many door closers use springs as the driving means because making the driving means electric may cause the door to close the passage during a power failure.
The embodiment shown in FIGS. 88 to 90 changes the vertical motion of the suspended weight as a means for urging the rotation that changes to a spring into a rotational motion via a pulley, and the urging force is increased with expansion and contraction like a spring. It does not decrease, the traction force of the weight is constant, and the force for energizing the rotation of the device can be kept constant. The embodiment of FIGS. 88 to 90 is characterized in that a weight is added by “switching means”.

Although the embodiment shown in the drawings of the present application uses a spring as the driving means, the present application does not limit the power of the driving means because a better result can be obtained when the electric motor is used than when the spring is used as the power.
For example, the “switching means” of the present invention operates largely to rotate the door small, and can be greatly decelerated by an electric actuator that rotates at a constant speed. This temporarily stops the door of the present invention before closing.
For example, when the spring is used as the driving means in the rotating mechanism shown in FIG. 13, the spring expands and contracts according to the load. Therefore, the “switching means” that does not apply the load expands and contracts in an instant, and the “switching means” is large. The operation ends in an instant. In other words, the spring is loaded and slowly expands and contracts only when the force to rotate the door is insufficient, but the "switching means" is a large force and a large operation that slightly rotates the door. Does not slow down at all. When the electric actuator that rotates at a constant speed is used as the driving means, the door is temporarily stopped before closing because the “switching means” slightly rotates the door with a large operation.

Patent Document 4 relates to a door of a product outlet of a vending machine. The door has a horizontal rotation axis, and has a door sealing and holding mechanism that has a small rotational moment at the initial stage of the door closing and a maximum at the final stage. It is to provide.
Basically, when the rotational axis of the rotating body is vertical, the rotational force acting around the rotational axis is equal to or greater than the rotational resistance around the rotational axis and constant throughout the rotation. On the other hand, when the rotating shaft is horizontal, the rotational force acting around the rotating shaft changes as the center of gravity of the rotating body moves horizontally. The distance L between the line of action of the force F acting on the rotating body and the rotation axis is constant in the former case and changes in the latter. Therefore, the latter is not provided with "rotating means in the range (a)" and "switching means" that keep the distance L small.

In Patent Document 4, a strong force is applied by the lever principle when sealed, and the “distance between the operating point and the fulcrum” decreases even though the spring force decreases as the door closes. This gradually increases the “force acting on the door”.
In Patent Document 4, the magnitude of the rotational force gradually increases or decreases as the lever fulcrum moves with the rotation of the rotating body. It does not change suddenly at a predetermined boundary as in the present application. Further, as in the present application, it does not deal with “a rotating body in which different rotational forces are applied to the end of rotation and rotation until then”.
In Patent Literature 4, “the force acting on the door” and the opening of the door are proportional. If the purpose is to make the opening of the door proportional to the “force acting on the door”, as shown in FIG. 1 (d), “a spring that is separated from the rotation axis of the door as the door rotates. ”Can be used to derive similar results. Also, by adjusting the stiffness of the spring, the magnitude of the force acting at the beginning and end of rotation can be freely designed.
That is, Patent Document 4 can be solved by a single spring as shown in FIG. The present invention includes “switching means” and cannot be solved by a single spring as shown in FIG.

Patent Document 5 relates to the opening of the entire surface of the high-frequency heating device. The rotation axis of the door is horizontal, and unlike Patent Document 4, the door is vertical when closed and the rotational moment is zero. There may be a “switching means”. Patent Document 5 ignores the balance of moments described above, and the damper is operated only in the “range (ii)”.
Patent Documents 4 and 5 are structures in which the lever's fulcrum moves with the rotation of the rotating body. This is a crank mechanism that changes the linear movement of the lever along the fulcrum to the rotational drive of the door. Energize in the moving direction. The action point and the door are connected via a link plate in Patent Document 4, and Patent Document 5 is directly connected.
In Patent Document 4, the rotation direction of the lever and the rotating body is opposite to each other. In Patent Document 5, since the lever and the rotating body are not connected by the connecting rod, the magnitude of the rotational force changes as the rotating body rotates. This is different from the present application.

Compared with FIG. 76 and Patent Document 4, in FIG. 76, the applied point is connected to the rotating body J, and the movement is constrained on the circular orbit, and the “rotating means in the range (A)” and the “(A) range” are compared. The distinction of the “rotating means” becomes clear, and the rotation of the rotating body J of the driving unit is small with respect to the large operation of the door D in “(range)”, and the link A functions as a lever only when closed. Moreover, the force of rotating the door is insufficient when the direction of the link AA is directed toward the door pivot O before the closing.
Compared with FIG. 76 and Patent Document 4, the configuration is almost the same, but in FIG. 76, the rotation direction of the door and the lever is the same, but Patent Document 4 is in the opposite direction.
As a result, in FIG. 76, the lever's fulcrum remains in the “(A) range” without moving, and a weak force continues to act on the door. At the end of the door rotation, the fulcrum moves and approaches the point of action.
On the other hand, in Patent Document 4, the fulcrum of the lever continues to move from the beginning to the end of the rotation of the door. It differs from the present application in that the magnitude of the rotational force acting on the door changes with the rotation of the rotating body and no “switching means” that suddenly changes at a predetermined boundary.
Since Patent Document 5 directly connects a lever and a rotating body (without inserting a connecting rod between them), the operation of the door becomes the lever operation as it is. The dampers shown in FIGS. 47 and 48 operate in a no-load state and greatly expanded rotation of the drive unit. Patent Document 5 itself resists the small rotation by the inertial force attached to the door itself. A simple damper is not effective.

Next, several examples of applying the “means of the present invention in which different forces act at the end of rotation” in industrial fields other than doors will be introduced.
The "means for applying a force having a different magnitude in each divided range" according to the present invention requires a force when it is necessary and requires a force when it is not necessary in other switchgears. And not to. For example, as illustrated in FIG. 94, a laundry basket is described as an example. The laundry basket is one of “two opening / closing bodies that share a rotation axis and rotate relative to each other”, and the laundry basket opens. Sometimes more than "the force to pinch the laundry in the bag" is required, but when the means of the present invention is adopted, the pinching force is released at the moment of opening from the closed state, and no force is required thereafter. To open. After the moment when the conventional laundry basket is opened from the closed state, the “force to open the laundry basket” gradually increases. (The embodiment of FIG. 94 uses the rotation mechanism of FIG. 67.)
The cutting rod described in FIG. 94 works when closed, and the force of the spring interferes with the work. For example, when the return spring is attached to the punching machine and the return after the punching is urged, the return spring interferes with the punching operation. Means are taken to disable the return spring.

Further, the present invention can be applied not only to a rotating body that rotates about a rotating shaft but also to a moving body that reciprocates along an arbitrary path. The sliding door illustrated in FIG. 90 is one of “two moving bodies that face each other along one path and approach or separate from each other”, and the sliding door illustrated in FIGS. Sometimes it uses a means to add new power.
The “means for adding a new force when working” is used in a normal press or shearing machine, and adds a new force when pressing with a clutch or the like. 90 (c) adopts the “means for moving the line of action of the force” so that the blade moves up and down in a linear reciprocating motion like a normal press or shearing machine. Can be employed.
By adding the link AA in the rotation mechanism of FIG. 13, the movement of the connecting axis C is not limited to the circular movement, but the movement along the linear trajectory as shown in FIG. Thus, the present invention is not limited to an opening / closing device having a rotating shaft, but can be applied to a machine that reciprocates like the above-described press machine or shearing machine.
The rotation mechanism shown in FIG. 37 is also a moving means, and is a moving mechanism that moves the center of gravity up and down with a constant force from the beginning to the end.

The embodiment shown in the drawings of the present application is divided into a range where work is performed and a range where work is not performed, and the magnitude of the force acting in each range is different, but most of the force works. In some cases, a small force is applied so as not to work as shown in FIGS. 94 (e) and 94 (f). Further, most of the shoes work when they are closed, and the shoe of FIG. 54 is an embodiment that works when the opening and closing body is opened.
Each of these embodiments includes the “rotating means in the range (A)”, the “rotating means in the range (I)”, and the “switching means” of the present invention, and the “force action line moves”. Means.

The "switching means" is characterized in that the magnitude of the force acting on the rotating body is switched from large to small or from small to large, with little or no rotation of the rotating body at the boundary between the two ranges. The feature of “switching means” is to bring about dramatic development in industrial machines other than doors.
This feature can be applied to a finger joint of a robot arm as described in FIG. When the movement of the finger joint is interlocked with the expansion and contraction of the spring as in the normal means, the distance between the finger to be gripped and the finger is reduced as the grip is strongly held, but the egg is crushed. By adopting a means that increases the strength of the spring without rotating the body, you can grab the egg with a strong force without crushing it.

Also, “the feature of the present invention in which the switching means operates largely with little or no rotation of the rotating body” is a powerful braking mechanism, and an object collides with the door D in FIG. When acting as a mechanism, the object's “small movement before the collision” is expanded and resisted by the long movement distance of the piston, so that the collision that makes the object's movement speed zero at the moment is decelerated over a long time Can be replaced. Also, it is a shock absorber that exerts its power during braking, not directly acting on the movement of the object and buffering, but delaying the operation of the device, and does not resist the carrying pressure of the object before the collision There are features.
The door of the present invention does not act on the rapidly rotating door and cushions it, but acts on a device that rotates rapidly against a door that does not rotate rapidly.

In addition, the feature that the “switching means” operates differently in the opening direction and the closing direction is that it exerts its power on the reduction gear. The device described in FIG. Therefore, there is a feature that the deceleration effect is not strong or weak by decelerating without accumulating the restoring force so as not to accelerate by reverse movement.
Thus, the speed reducer which continues buffering small to continuous rotation can be employ | adopted for a silver car, for example, and is suitable for the speed reducer of the grade which does not accelerate when going down a gentle slope.

The “switching means” includes the opening degree of the door when the door is switched from the “rotating means in the range (A)” to the “rotating means in the range (I)” in the process of closing the door, and the process of opening the door. There is a feature different from the opening degree of the door when switching from “rotating means in the range of (ii)” to “rotating means in the range of (ii)”. This feature will revolutionize the speed reduction mechanism of the door closer closing device.
There is a difference in the rotational speed of the door when it is closed when the door is wide open and the hand is released and when it is slightly opened and the hand is released. The inertial force attached to the door varies depending on the opening of the door when the hand is opened and released. The above feature makes it possible to decelerate by applying a brake when the door is widely opened and released, and to be sealed without applying a brake when the door is slightly opened and released.

Decreasing the speed by applying a brake reduces the force that rotates the door, and in the door closer that does not have the above characteristics, the force that rotates the door is maintained even if the urging force of the door is reduced by applying the brake. However, by having the above-described feature, the urging force of the door may be reduced so that there is no force for rotating the door. In the present invention, the speed reducing means that acts immediately before closing is not one that further increases the strength of the spring as in the “door closer equipped with a hydraulic cylinder”, and the door is sealed even with a weak spring. The present invention is different from other door closer speed reducing means in that the “brake applied immediately before closing” of the present invention does not increase the strength of the spring.
In the process of closing the door, the door rotates with inertial force even when there is no force to rotate the door, but in the door closer having the above characteristics, the door is opened within the range that continues to rotate only with this inertial force. Sometimes even if you let go of the door, the door will not stop.

As described above, the "switching means characterized in that it operates greatly with a slight rotation of the rotating body or a slight movement of the moving body" and "rotating means within the range (A)" and "rotating means within the range (ii)". The present invention, which is only provided with "means", replaces a "door that moves only with a spring" that has not been able to replace "a door closer with a hydraulic cylinder" so far into a "door that closes slowly and securely seals". Needless to say, this will not only make it possible, but it will also build a firm position in industrial fields other than doors.

The situation before the sealing of the present invention is that the door is stopped or barely moving, and the force for rotating the door is insufficient, and a large force is required when sealing. , "It must be tightly sealed with the force of a small spring."
The sealing mechanism shown in FIG. 15 is a “mechanism for rotating a cam wheel with a cam wheel at the tip” that “supports a large force in the radial direction and seals it with a small force in the circumferential direction”. It has the feature of supporting the force and rotating with a small force in the circumferential direction.
This feature will be compared with the prior art.

Patent Documents 6 to 12 are “rotating mechanisms including cam sliding surfaces and cam wheels that move along the same” as in the rotating mechanisms of FIGS. 35 to 37, in which the rotating shaft is horizontal and the center of gravity is up and down. However, in Patent Documents 6 to 8, the rotational force suddenly changes at a predetermined boundary, and the “force to rotate the rotating body at the end of rotation” The differences are the same as in the present application.
In Patent Document 6, the shape of the intermediate portion of the cam body sliding surface shown in FIGS. 35 to 37 is a circle, and even if the rotating body is rotated at the end of the rotation, the rotational force does not act on the rotation so far. And different. Further, although the wheel is locked at the end of the sliding surface, the sliding surface does not function as a lever at the end of rotation as in the present application.

Patent Document 7 relates to a hinge of an automobile trunk lid, Patent Document 8 relates to a lid of a copying machine, Patent Document 9 relates to an opening / closing device for a back door of the automobile, and Patent Document 10 relates to a undulation gate.
Patent Documents 7 to 10 relate to a lid whose horizontal axis is horizontal and opens and closes up and down, and is urged in a direction to support the lid so that it does not drop when rotating in the closing direction. The direction is reversed.
An opening / closing device having a horizontal rotation axis stops the rotation by an urging force in a direction opposite to the rotation direction. The switchgear whose rotation axis is vertical is rotated by force.
When the design of the switchgear in which the rotation axis is vertical and the switchgear in which the rotation axis is horizontal are redesigned, the switchgear in which the rotation axis is vertical The lid is lowered by supporting it with a force equal to or less than the “required force”, and a slight biasing force is applied in the downward direction to rotate the lid downward.
As described above, the structure and operation differ depending on whether the rotation axis is horizontal or vertical. The rotation mechanism of the switchgear changes the structure and operation at the design stage. The mechanism is independent of whether the axis of rotation is horizontal or vertical. This application is applied also to the rotation which does not accompany the rotation accompanying the vertical movement of the center of gravity.

In Patent Document 7, the force that acts at the end of rotation when the lid rotates in the opening direction is the same as the rotation direction until then, but holds the stop position, and the rotation is stopped at the end of rotation. Does not work. The end of rotation is different from the present application.
In Patent Document 8, the force acting at the end of rotation when rotating in the direction in which the lid is closed is different from the rotation direction so far. The end of rotation is different from the present application.
“Rotating mechanism with cam wheel and cam sliding surface”, but at the end of the rotation as in the present application, the rotating body is rotated by the “distance between the action line of the pressing force and the center of rotation”. It is not a mechanism.
In Patent Documents 7 to 10, a cam wheel is attached to the tip of an elastic body that is also an urging means, but in FIGS. 35 to 37, a cam wheel is attached to the tip of a link that is rigid and does not deform. The springs of Patent Documents 7 to 10 replace the cam wheel rotating body shown in FIGS. 35 to 37 with a cam wheel attached to the tip thereof.

The comparison between Patent Document 8 and FIGS. 35 to 37 will be described later with reference to FIG. 95. Differences between Patent Document 8 and FIGS. 35 to 37 will be described.
In Patent Document 8, the cam wheel moves along the cam sliding surface by the expansion and contraction of the spring, but the action line of the force of the spring does not directly rotate the spring through the rotation axis of the spring. Therefore, it is different from the present invention in which the magnitude of the force acting on the rotating body is controlled by adjusting the “distance between the force acting line and the rotating shaft”.
In Patent Document 8, the force of the spring is broken down into “a force acting perpendicular to the cam sliding surface” and “a force acting parallel to the cam sliding surface”. “The force acting at right angles to the cam sliding surface” is “the force by which the cam wheel B presses the cam body sliding surface”, and is a force that is not involved in the movement of the cam wheel. “The force acting in parallel with the cam sliding surface” is a force for moving the cam wheel along the cam sliding surface. In Patent Document 8, a part of the spring force changes its direction to rotate the spring and move the cam wheel. Patent Document 8 links the movement of the cam wheel and the rotation of the lid. The cam wheel is accommodated in a long hole provided in the lid of the copying machine, and the cam wheel moves along the cam sliding surface. As a result, the lid of the copying machine rotates.

35 to 37, “the force that the cam body sliding surface presses the cam wheel B” does not pass through the rotating shaft of the cam wheel rotating body, so the cam wheel rotating body is directly rotated and the force to rotate the cam wheel rotating body is “ It is proportional to the distance between the “force for pressing the cam wheel B” and the rotating shaft of the cam wheel rotating body. “The force that the cam body sliding surface presses the cam wheel B” is “the force that works at right angles to the cam sliding surface and does not participate in the movement of the cam wheel” and “the force that works parallel to the cam sliding surface”. Therefore, the cam wheel rotating body rotates with a “small force perpendicular to the shaft” while supporting a large force on the shaft. In Patent Document 8, this characteristic is not recognized.

In Patent Document 8, the biasing means for rotating the lid is a spring, and the closer the cam body sliding surface and the spring are in a parallel state, the smaller the force the cam wheel moves and the lid rotates. In FIGS. 35 to 37, the force for rotating the cam wheel rotating body is a “force for pressing the cam wheel B”, and the closer the cam body sliding surface and the cam wheel rotating body are in parallel, the larger the force. The cam wheel moves and the cam wheel rotating body rotates.
In Patent Document 8, the force of the spring for rotating the lid is large when the cam body sliding surface and the spring are close to a right angle. In FIGS. 35 to 37, the cam body sliding surface and the cam wheel rotating body are used. When the angle is close to a right angle, the pressing force for rotating the cam wheel rotating body is small. In Patent Document 8, the result is opposite to that in FIGS. Therefore, it is not intended to rotate with the weak spring force as in the present application.

The following Patent Documents 9 to 10 and the present application are greatly different in effect depending on whether or not there is a characteristic of “rotating with a small force perpendicular to the shaft while supporting a large force with the shaft”. Become.
In Patent Document 9, a back door of an automobile is moved up and down by a “damper paste that expands and contracts by air pressure”. As the back door is opened, the roller moves away from the vicinity of the back door as the back door is opened, so that the moment due to gravity acting around the rotation axis of the back door and the air pressure of the damper Is to balance.
The spring of Patent Document 9 pushes up the back door with a large force against the weight of the back door, and the force for biasing the back door is large. On the other hand, when the rotating mechanism of FIGS. 35 to 37 is used as the moving means in the vertical direction of the back door, the weight of the back door is supported by the rigid portion in the axial direction of the cam wheel rotating body. The cam wheel rotating body is rotated by a small force perpendicular to the axial direction to move the back door up and down, and the force for biasing the back door is small.

Patent Document 10 relates to a hoisting gate, and the hoisting gate includes a door body 4 having a water stop plate and a door body 21 that supports the door body 21, and the door body 21 is similar to the cam wheel rotating body Jq of FIGS. A cam wheel is provided at the tip, and the cam wheel moves along a sliding surface provided on the door body 4 to make the door body 4 stand up or lie down. However, in Patent Document 10, the door body 4 is orthogonal to the door body 21 in the standing state, and the door body 4 is parallel to the door body 21 in the lying state, so the door body 21 does not weight the door body 4 in the axial direction. Since it is supported in a direction perpendicular to the axis, the rotation urging means of the door body 21 supports the weight of the door body 4. Therefore, the urging force for raising the door body 4 is increased. It is not a structure that is orthogonal to the sliding surface when lying down, such as the cam wheel rotating body of FIGS.

97 to 102 are embodiments in which the present invention is applied when the rotation axis is horizontal, and is an apparatus that operates with the rotation mechanism of FIGS. However, the weight of the lid is supported by the axis of the cam wheel rotating body, and the lid is moved up and down by rotating the cam wheel rotating body with a small force. Further, they are characterized in that they support the weight of the lid in the axial direction of the rigid body, and the axis of the rigid body is substantially perpendicular to the lid when the lid is in a lying state and substantially parallel when it is in an upright state. Unlike Patent Documents 9 to 10, there is a “feature with a small biasing force”, and the weight of the lid is not supported by a large biasing force as in Patent Documents 9 to 10.
Thus, the present invention makes it possible to support the weight of a large structure and move it at the same time, and the structure supporting the weight is structurally mechanically stable and does not move with the weight. Regardless, it is characterized by its ability to easily move heavy objects with a small force.

In this way, a transmission means that exerts a large force on the door, such as “rotating means in the range (A)”, is a means that acts on a door with a small force when used from the opposite standpoint. It can be used for the device to do.
In particular, the rotation mechanism shown in FIGS. 35 to 37 is a rotation transmission mechanism in which a constant pressing force acting on the outer edge of the rotating body and a constant rotational force acting around the rotating shaft of the rotating body are balanced. By applying a substantially constant rotational force from the beginning to the end of rotation, a constant pressing force acting on the outer edge portion continues to act on the object (the above-mentioned moving body), and from the beginning when the object starts to move to the end when the movement ends. It also serves as a moving means for moving a certain force. 35 to 37 is a moving means that rotates with a small force while supporting a large force in the axial direction, like the sealing device often found in the embodiments of the drawings. There is a feature that supports the weight of.

FIG. 100 is a moving device based on the rotation mechanism of FIG. 37, and as described with reference to FIG. 80, the lid W is horizontally leveled with the smallest force by keeping a constant rotational force around the rotation axis Qj of the cam wheel rotor. It can be rotated from the state to the suspended state. When a constant constant force continues to act on the moving body, the force required for movement is the smallest.
97 to 99, the center of gravity of the lid moves horizontally as the lid W rotates, and the rotational moment acting on the rotation axis Q of the lid changes. In the case of FIG. The contact point b that supports the weight of the lid also moves horizontally in accordance with the horizontal movement, and a constant rotational force continues to act around the cam wheel rotating body rotation axis Qj, so that the moment around the lid rotation axis Q is substantially balanced. When the lid W can be stopped at any position from the horizontal state to the suspended state in this way, no force is required to open and close the lid, and the lid can be felt lightly.
Patent Document 11 relates to “a wheel having an outer periphery with a plurality of wheels attached to the outer edge portion and having a spiral curve shape”, but this recovery spiral curve is not the involute of FIG. 100. The spiral curved wheel is the same as the involute of FIG. 100 in that it rotates with a small force while supporting a large force with an axis.

FIG. 102 is a gate that rotates on the axis of rotation that is floating on the water surface and is fixed to the quay, and is a device that generates electricity by rotating with the flow of water. Then, even if a large water pressure acts on the gate due to the water flow, the rotation mechanism shown in FIGS. Can be moved easily with force. The power generation device of FIG. 102 disables the rotation mechanism of FIGS. 35 to 37 and causes the gate to move with water pressure, and enables the rotation mechanism of FIGS. 35 to 37 to prevent the water pressure from acting on the gate. Against this, the gate is returned.
In this way, “a rotating body that rotates with a small force while supporting a large force in the axial direction” derives a large action with a small force, but it is also difficult to move when it receives a force. It is a disadvantage that it does not move even if it is received. In FIG. 102, when the rotation mechanism of FIGS.

The rotation mechanism of FIGS. 35 to 37 is a rotation mechanism in which the rotation axis is vertical and balances with the rotation resistance around the pivot axis. In the rotation mechanisms of Patent Documents 9 to 10, the rotation axis is horizontal and the center of gravity moves horizontally. This is a rotating mechanism that balances the changing rotational moment. Both are rotation mechanisms related to the balance of rotation moments acting around the rotation axis, and the sliding surfaces are designed to balance different rotation moments and have different shapes. Patent Documents 9 to 10 and FIGS. 35 to 37 are not merely changes in the shape of the sliding surface so as to be balanced with each other at the design stage, but are different in structure and function as described above.
In the former, there is a problem that the force leads to acceleration. There is a “switching means” between the “rotating means in the range (A)” and the “rotating means in the range (I)”. The processing of inertial force is a problem for “means” and its surroundings, but the latter is not a problem. Therefore, it is natural that the latter technique does not include a “switching means”.

The latch device shown in FIGS. 41 and 42 has a feature of “rotating with a small force perpendicular to the shaft while supporting a large force with the shaft”, and prevents the closed door from opening.
When the closed door is prevented from opening, the “force to open the door” acts in the radial direction of the latch, and the rotating shaft of the latch receives this.
When the door closes, the “force to close the door” acts at right angles to the door surface, and a normal latch moves linearly in a direction perpendicular to it, and a large force is required to dent the latch inside the door. is necessary.
In the present invention, the “force for closing the door” rotates the latch. Even if the force acting in the circumferential direction of the latch is small, the latch rotates and locks the door. Therefore, no great force is required to dent the latch inside the door.

The present invention is such that when passing through a door equipped with a conventional door closer, the door is not opened against the resistance of the door closer, but is allowed to pass through the door portion with low resistance. It is desirable to open and close it freely like an electric door.
The ideal door of the present invention is a “door that does not feel the strength of the spring when it is opened”, and the strength of the spring is as small as possible. The strength of the spring is determined by the force required at the time of sealing. For a door that is closed by a magnetic catch, the force acting on the door does not need to increase at the end of rotation. This rotates with "a force slightly exceeding the maximum static frictional force of the door" and does not require any more force.
However, a door that is closed with a magnetic catch cannot be unlocked without turning the handle, and cannot be locked.
Patent Document 12 relates to a latch structure for preventing breakage, and the latch bolt of the document rotates but also retracts. The resistance at the time of closing is not reduced like the latch device of the present invention. Further, there is no feature of receiving the force that prevents the door from being opened on the side surface of the concave portion that accommodates the latch claw, not the rotation axis of the latch claw.

Patent Documents 13 to 15 are sealing devices that operate only at the time of sealing. When opened, they are separated from the door and do not participate in the rotation of the door. The swing arm generally includes a swing arm that reciprocates between a stationary state and a closed state, and a return spring that operates to the closed state and returns to the stop state. Is moved from the stationary position to the closed position.
In order to stretch the return spring, a large force is required, and the device does not start in a state where there is no force to seal the door at the end of the rotation of the door as in the present invention.
In the first place, it is a device that seals an accelerated door while decelerating, and is designed to operate when the force to stretch the return spring is sufficient, like an accelerated door. Or it is designed to operate by pushing the door in with a human hand.

Patent Documents 13 to 15 are sealing devices that operate in a “range from immediately before closing to the time of closing (i)”, and do not include “rotating means in the range (a)”. These devices are devices that close when the passerby pushes and closes or decelerates the accelerated door, and are not devices that are closed from full open.
1 seems to be the device of the present invention when one spring shown in FIG. 1 is attached to this device, but the rotational force of the spring is insufficient just before closing as in the present invention. It is a device that stops if it decelerates, and seals the door that rotates with a weak force, and “functions in a state where a weak rotational force is working. Patent Documents 13 to 15 are strong forces. The door is rotated or braked or decelerated.

As illustrated in FIGS. 2-17, the present invention allows the device to continue to operate even if the door stops. In the case of a normal link device, the rotation of the driving unit and the rotation of the driven unit are in a one-to-one correspondence relationship, and the operation is linked, but the “switching means” operates regardless of the rotation of the door, For example, as shown in FIGS. 10 to 12, the connecting shaft is movably attached at the connecting portion of the link, and as shown in FIG. 13, it is rotated close to the opening direction before closing, as shown in FIGS. By using one of the links as a spring, a link device that does not stop even when the door stops is realized. In FIG. 18, even if a spring is attached as in Patent Documents 13 to 15, the sealing device does not move if the door stops.

Patent Documents 13 to 15 are the same as the present invention in that they include a “sliding surface and a slider that moves along the surface”. However, the door is sealed under a large force, as in the present invention. Even a small force does not seal the door.
When the devices of Patent Documents 13 to 15 are sealed, they are structurally unstable, and the fulcrum supporting the reaction force of the sealing force moves. Only a part of the spring force is used as the sealing force. Not used.
On the other hand, in the present invention, as shown in FIG. 15, the action line of the force that the sealing force acts at the time of sealing approaches the state where the axis of the rotating body is in a straight line, and approaches the state where the link device is stationary. The reaction force of the sealing force is supported.
Only when the node of the structure does not move, the node force works, and the spring force works as a sealing force. When the device can move, the force acts weakly, and when it cannot move, the force acts strongly.

Patent Document 13 is provided with a groove on one side of the door and the door frame with rotation and a pin that moves along the groove on the other side, and each corresponds to the cam body sliding surface and the cam wheel of the present invention and has the same function. Yes. Patent Documents 13 and 14 include “pins and grooves” corresponding to “wheel B and sliding surface K that moves along the wheel B” of the sealing device of FIGS. 14 to 17, and slide around wheel B as shown in FIG. 45. The moving surface K (hereinafter, the sliding surface K is a sliding surface K or a cam body having the sliding surface K) rotates, and the groove rotates around the pin.
In FIG. 45, the straight line connecting the “contact point b between the wheel and the sliding surface” and the rotation axis of the link A is substantially perpendicular to the “closed door surface”, and “the sliding surface K presses the wheel B”. The action line of “force to do” is close to the rotation axis of the link A. Therefore, even if the link A in FIG. 45 rotates with a small force, a large force acts on the door to seal the door.
On the other hand, Patent Documents 13 and 14 disclose that the axial center line of the groove (hereinafter referred to as the axial core line is a straight line connecting the point of action of the rigid body force and the rotational axis of the rigid body with respect to a certain rigid body, or both ends of the rigid body. The axis of support is a parallel part of the female part) and is substantially parallel to the “closed door surface”, and the action line of “the force by which the groove presses the pin” is far from the rotational axis of the groove. Therefore, even if the link A groove rotates with a great force, the force acting on the door is small, and the spring force for sealing the door needs to be large. Similar to Patent Document 10, the rotational force itself acting around the rotational axis of the groove is a sealing force, and is sealed with a strong spring force.
Since the strong spring keeps the stationary state during standby, it is necessary to apply a large force to start the groove, and the force does not start unless a force that generates a large impact sound is applied. This is different from the embodiment of FIG.

In the sealing device of FIG. 15, the wheel presses the sliding surface. In the sealing device of FIG. 45, the sliding surface presses the wheel. In either case, the “contact point b between the wheel and the sliding surface” moves largely parallel to the closed door surface, and moves small in the direction perpendicular to the closed door surface. In Patent Documents 13 and 14, the range of the circular motion of the contact point b is different, and is performed in a range in which the contact point b largely moves substantially at right angles to the closed door surface. That is, the door moves in the closing direction. It moves small in the direction perpendicular to the closed door surface.
The sealing device shown in FIG. 15 generates a large force with a small force by changing the direction of the force to a perpendicular direction. It is a force conversion device like the so-called wedge effect. In the cam wheel rotary body sealing device of FIG. 15, the cam wheel rotary shaft has a rotating shaft, and in the wedge effect sealing device of FIGS. The entire apparatus is in a mechanically statically stable state where it does not move.
The structure in which the contact b moves easily as in the sealing devices of Patent Documents 13 and 14 is a structure that is structurally stable, and a structure that is easy to move cannot act or accept a large force. If it receives a large force, it will move, and it will not accept a large force. Even if the force converted into motion works statically, no large static force is generated.

However, when the closed door is opened, the contact b moves small in the opening direction even if it moves largely parallel to the door surface. This means that a resistance is applied when opening, and it moves linearly in parallel with the door surface as shown in FIG. 49 and does not open when the moving distance is long. In Patent Documents 13 and 14, when the closed door is opened, the contact b greatly moves in the direction in which the door is opened, so that no resistance is applied when the door is opened.

The present invention requires measures to eliminate the “defect that the door does not open”. In FIG. 15, the shaft core line Zj of the rotating body J can be made perpendicular to the closed door surface so that the sealing force acts greatly. When opening the door that is close and close, the shaft center line Zj of the rotating body J is slightly moved to the closed door surface so that as soon as the door is opened slightly, the wheel moves to a position more easily separated from the closed door surface. The position is not set at a right angle.
In FIGS. 59 and 60, the wheel B moves largely parallel to the closed door surface and seals on the principle of leverage, but the mechanism for sealing and opening the door is both disclosed in Patent Document 13, 14 is the same as the mechanism for sealing and the mechanism for opening, and the lever and the groove at the time of sealing have substantially the same rotation angle with respect to the “closed door surface”. The levers of FIGS. 59 and 60 are rotated when the door is opened in the same manner as the grooves of Patent Documents 13 and 14, so there is no resistance when opening the door.

FIG. 21 shows a case where the wheel Bb is in contact with the “corner between the sliding surface substantially perpendicular to the closed door surface and the sliding surface substantially parallel to the closed door surface” to be sealed. When the door is opened, the wheel Bb moves largely at a right angle to the door surface that is immediately closed away from the corner, so there is no resistance when opening the door.
The sealing device of FIGS. 21 and 50 engages the sliding surface only when the wheel is sealed, and the other parts are detached. However, the wheel of the sealing device of FIGS. In addition, the “switching means” moves along the door frame from a position near the pivot axis O of the door to a position far from the door frame O, and moves largely in parallel with the door frame within a range not leaving the door frame. When opening the door, the wheel must not only move away from the door frame, but also move largely parallel to the door frame to approach the door pivot axis O. For this reason, the sliding surface K is not fixed, but is attached rotatably.

The sealing device of FIGS. 21, 49, 50, 114, and 115 is such that a strong force is applied only at the moment when the latch is recessed and accommodated in the door frame, and the strong force is immediately released when the closed door is opened. I try to do it. The sealing device of FIGS. 114 and 115 not only rotatably attaches the sliding surface K, but also fixes the sliding surface K after the latch is recessed and accommodated in the door frame, and is strong at the time of sealing. Power is released. When opening a closed door, little force is needed to open the door, since the door does not have a sealing force.
In Patent Documents 13 and 14, resistance is not greatly applied when a closed door is opened, and such measures are not necessary. In addition, there is no means for applying a large force with the lever function.

Patent Document 15 is a shock absorber for a door. When the engaging member 7 prepared on the side of the door and the recess prepared in the door frame are sealed, the engaging member 7 rotates in the same manner as in Patent Document 12. To do.
Patent Document 12 is a locking device, and Patent Document 15 does not have a locking function. The latch device of Patent Document 12 is also a sealing device in a broad sense having a reverse rotation preventing function. However, Patent Document 15 does not have a feature of receiving a locking force in the circumferential direction.

Patent documents 13 to 16 are a door sealing device and a shock absorber as well as the present invention, which work within the range of (i) and decelerate the door during a slight rotation of the door. Adds resistance close to collision. In particular, when it is not attached to a position close to the pivot axis O of the door as in the present invention, but is attached to the door side surface on the handle side, the engaging member prepared on the door side surface engages with the concave portion prepared on the door frame. The distance is so short that it only collides before the door hits the door.
Patent documents 13 to 16 work directly on a door that closes rapidly to decelerate the door just before closing. Even if the rotational speed of the door just before closing is slow as in the present invention, it does not decelerate.
In Patent Documents 13 to 16, when the rotational speed of the door immediately before closing is slow as in the present invention, the rotation of the door may be stopped, and if it remains stopped, it will not be closed again.
On the other hand, the sealing device of the present invention is designed to continue to move even when the door is stopped, and when the rotational speed of the door immediately before closing exceeds a certain speed as illustrated in FIG. It is designed to stop operation and start again when the door stops rotating.
As shown in FIG. 13, the link device that operates in the direction in which the door opens just before closing, and the sliding surface that works in the direction in which the door opens as described in FIGS. The braking force also increases according to the magnitude of the inertial force attached to the door. Again, when the door stops rotating, it starts again.

The operation of the shock absorbers of Patent Documents 13 to 16 is interlocked with the rotation of the door, and the rotation of the door is directly the rotation of the shock absorber. On the other hand, the closing device of the present invention continues to operate even when the "switching means" stops rotating the door, and merely increases the time required for the operation of the "switching means".
As in the shock absorbers of Patent Documents 13 to 16, the door is separated within the range (A) and engaged within the range (B). However, the opening / closing device of the present invention causes the door to rotate greatly within the range (A). However, since the operation of the device is slow and slow, the door rotates little and the device operates largely in the range of (i), a damper is attached to the opening and closing device of the present invention so that the operation reaches the range (a). However, the damper works in the range of (A) and works effectively in the range of (I).

In the operation of “switching means”, when the action point staying in the vicinity of the pivot axis O of the door moves away from the center of rotation, the door does not rotate, so the spring force does not need to rotate the door and the action point is unloaded. In a moment, move away from the center of rotation.
The present invention decelerates even when the door stops immediately before closing, as in Patent Documents 13 to 16, and the operation of the closing device is instantaneous in an unloaded state. It corresponds to a wide range from when the process ends to when the door is subjected to a heavy wind and is subjected to a large impact.
Patent Document 16 is a speed reducer that utilizes the magnitude of centrifugal force depending on the closing speed of the door, but the inertial force attached to the door varies depending on the opening of the door that opens the door and releases the hand, and the range in which this speed reducer operates is as follows. Only when the centrifugal force is large.

47 and 48 show an embodiment in which a damper is attached to the closing device of the present invention, which acts as a “switching means” to slow down the operation of the closing device, as in the shock absorbers of Patent Documents 13 to 16. It does not work directly on the door, and does not resist door rotation.
Neither the damper of the present invention nor the device that prevents the rotation of the door will result in an increase in “strength of the spring that rotates the door”. Further, since the damper has a weak spring force for driving the device, a simple damper with low air pressure can function sufficiently.

The object of the present invention is to “make the door not feel heavy” when the door is opened. When opening a closed door, the door will not open unless a force equal to the “force for closing the door” is applied in the direction opposite to the sealing force. Even if the spring force is weak, if you seal it with a strong force, the door feels heavy when you open the closed door despite the weak spring force.
The force to push the “door that is stationary with the latch abutting against the door frame W” to dent the latch and to bring the door into close contact with the door stop is “the door that moves with the latch abutting against the door frame W”. Much smaller than the force to push in and seal the door. When inertial force is involved in the sealing of the door, the “force for closing the door” is reduced by the amount related to the inertial force.
Since the inertia force disappears in the closed door, the door does not feel heavy when opening the closed door. Especially when the door is heavy, moving only a small distance, the dynamic inertia is large enough to dent the latch inside the door, so the strength of the newly added spring before closing is reduced, or The force when opening a closed door that is zero is reduced accordingly.

In this way, it is desirable that the inertial force is actively involved in the sealing of the door, but if the inertial force exceeds the “force to seal the door”, the exceeding force appears as the magnitude of the impact sound. Accordingly, means for reducing the inertial force is required.
Therefore, "means for measuring the magnitude of inertial force" attached to the door is necessary, and "means for measuring the magnitude of inertial force" is the structure of the switchgear depending on whether the inertial force is attached or not. Must be different, or the movement of the switchgear must be different so that the distinction can be discriminated. The distinction must be linked to the reduction gear.
Furthermore, it is necessary to adjust the magnitude of the braking force in accordance with the magnitude of the inertial force so that the magnitude of deformation of the switchgear follows the “magnitude of the inertial force”.

78 is a sealing mechanism composed of a cam wheel B and a sliding surface K. The sliding surface K is rotatably attached to the door frame W, and a spring is attached around the rotation axis of the sliding surface K to slide the sliding surface K. As the moving surface K rotates and the spring expands and contracts, “the inertial force that attaches to the door immediately before closing” is absorbed, and “the magnitude of the inertial force that attaches to the door immediately before closing” indicates the sliding surface K The evaluation is based on the size of the rotation angle. However, when the inertial force disappears, the sliding surface K rotates to return by the restoring force of the spring, and when the rotating body J rotates and the operation of sealing the door is delayed, the sliding surface K is rotated in the opening direction.
44, 45 and 104 are means for preventing the door from being sealed immediately before the closing dimension, and for temporarily closing the door before the closing dimension. If the delay means is not attached, the wheel B idles on the sliding surface K at the moment when the wheel B comes into contact with the sliding surface K and the door stops, and passes the entire length of the sliding surface K instantly. Become.

In order to prevent this from happening, the means described in FIG. 6 is to prevent the wheel from pressing the sliding surface suddenly immediately before closing, and the door to accelerate rapidly to pass the entire length of the sliding surface K in an instant. The connecting shaft C is rotatably attached to the door D, a spring is attached around the connecting shaft C, the wheel B continues to contact the sliding surface K, the door immediately before closing is stopped, and the door is gradually opened. It is a means for growing the "sealing force".
As in FIG. 6, the connecting shaft C is rotatably attached to the door D in FIGS.
The means described in FIG. 105 is a sealing mechanism in which the wheel presses the sliding surface. The wheel rotates after passing through the entire length of the outer edge of the sliding surface K, and the wheel rotates from the circumferential direction of the sliding surface K. Means for changing the path in the direction, and when the wheel enters between the radial path of the sliding surface K and the door frame W, the spring force is dispersed and the sealing operation is delayed. .

The force that pulls the door with the inertial force is smaller than the force that pulls the door that is not attached. By measuring the force that pulls the door, you can measure the magnitude of the “inertial force that attaches to the door”. .
51 and 52 evaluate the force for pulling the door by the magnitude of deformation of the “spring attached to the connecting portion for pulling the door”. When the spring is largely deformed, the stop device works and the spring is deformed. If it is small, the stop device will not work.
Such a measuring means can also be seen in a device that detects the speed of movement of an elevator, but even if it can be measured when the door is subjected to a heavy impact due to a strong wind, the operation of the closing device can be performed. When the process ends in an instant in an unloaded state, the spring does not significantly deform, and the magnitude of the braking force cannot be adjusted according to the magnitude of the inertial force.

The means described in FIGS. 106 to 109 is a sealing mechanism in which the wheel presses the sliding surface, and the wheel or sliding surface that is attached to the door or the wheel or sliding surface that is attached to the door frame is movably attached. ,
The wheel or sliding surface that is movably attached contacts the door frame or the stationary part just before closing, and stops the movement so far, thereby creating a gap between the part that continues the movement and the part that does not continue the movement. Thus, it is a means for measuring the magnitude of the “inertial force attached to the door” with the size of this interval.
For example, in FIG. 106, the sliding surface K is rotatably supported by the connecting shaft P at the tip of the link A that is rotatably supported by the door, and the tip of the sliding surface K contacts the door frame W. Thus, the link A rotates, and the magnitude of the “inertial force attached to the door” is measured by the rotation angle of the link A.

110 and 111 show that the moment when the hand is released from the door, the magnitude of the “force acting on the door” is set to the maximum static frictional force, and when the door starts moving, the movement frictional force is increased to accelerate the door. It is a means to make it smaller.
112 and 113 absorb the “inertial force attached to the door immediately before closing” by rotating the sliding surface K and expanding and contracting the spring, but the inertial force disappears and the sliding surface K is restored by the restoring force of the spring. It is means for preventing the door from rotating in the opening direction even if it rotates back.
114 and 115 are means for opening the door in a state where the sealing force is released and the sealing force is not applied at the same time as the door is sealed.

As described above, FIGS. 85 to 87 provide a mechanism that opens freely when the hand is released from the door, and a new device is added even if a new function is added. Instead, it provides a door that swings between two stationary positions so that the spring can be fully opened when opened slightly and closed when closed slightly.
Patent Documents 17 to 19 relate to “a door in which the biasing direction of the spring is separated into an opening direction and a closing direction with a certain opening angle of the door as a boundary”, and is based on the negative biasing force of the spring as a means of being stationary at the fully opened position. The means for reversing the direction of rotation of the door is only brought to the center when fully opened and closed.
As in the present invention, it does not deal with “a door that opens freely until it is fully opened when the fully closed door is opened slightly, and that is closed until it is fully closed when the fully opened door is slightly closed”. Further, in Patent Documents 17 to 19, “the opening angle of the door that is divided into the opening direction and the closing direction of the spring” is the same when the door is opened and when the door is closed. It differs from when it closes.
Since the force to rotate the door is small, it is not necessary to store as much force as the left to store the “power to open it freely until it is fully opened” with a slight rotation when the door is opened slightly. The same applies when closing the door a little.

JP2006-9547 JP 2005-273199 A JP-A-9-177425 JP 11-50734 A JP 2006-145068 A JP 2006-306359 A JP 62-59785 A Shokai 61-86732 JP-A-4-325314 JP2007-70924 JP 2006-306368 JP-A 62-178675 JP2007-120140 JP2007-177459A JP 2003-286787 A JP 2006-144419 A JP2007-39911A JP2007-332646A JP 2003-129741 A

A range of work in reciprocating motion of two opening / closing bodies that share a rotation axis and rotate relative to each other, and two moving bodies that face each other along one path and approach or move away from each other; It is a means to divide the range into a range that does not, and to make the magnitude of the force acting in each range different, the magnitude of the force at the boundary between the two ranges by the movement of the point of action of the force or Means are provided for switching from large to small or from small to large by changing the direction of the line of action of the force.

That is, the present invention is a rotation control mechanism in which “forces acting on a rotating body” F and M change in proportion to or in inverse proportion to the magnitude of L in accordance with the relational expression M = F × L described above. “Rotating means in the range of (A)” that makes the force act on the rotator small “Rotating means in the range of (i)” and “Switching means” that make the rotator work even on a small force.
The feature of the present invention is that the unnecessary force is removed from the reciprocation between the motion that does work and the motion that does not work, and every switchgear and reciprocating device "makes big work with a small force", and a small force is efficiently rotated. In many cases, a large force is applied at the end of the rotation, and the "rotating means in the range (A)" works to rotate the rotating body with a small motion, "Rotating means in the range of (ii)" works to rotate the rotating body small by operating largely.

The “switching means” is characterized by having no or little rotation of the rotating body, and continues to operate even if there is no force to rotate the rotating body. Switch to “Rotating means in the range of (i)”.
The feature that the “switching means” does not or hardly accompany the rotation of the rotating body means that the switching means operates greatly with respect to a small rotation of the rotating body. Is a means for allowing a large force to work with a small force, and means that the rigid body has a feature of supporting a large force in the radial direction and rotating with a small force in the circumferential direction.

According to the present invention, the robot arm that can grab eggs softly, the shoes that can jump freely in the basket court, the transport device that can lift the object lightly, the tide and the one-way flow of the river A power generator that can extract electric power is realized.
The present invention is applied to “another rotating device including a door” and brings about an effect.

When the door is closed, a force greater than “force necessary to seal the door” is applied, and when the door comes into close contact with the door stop, the kinetic energy held by the door is converted into an impact sound. The impact sound at closing is proportional to the square of the rotational speed of the door, and if there is a slight difference in the rotational speed of the door, the impact sound becomes extremely loud. In order to minimize the rotation speed of the door, if the door is rotated with as little force as possible, the door may stop before closing, and if the door is rotated with a large force so that it does not stop, The impact sound when closing is increased.
The problem to be solved by the present invention is mainly “how to reduce the impact sound at closing”, and the present invention is in the “range from fully open to immediately before closing (A)”. , The force acting on the door is "the force necessary and sufficient to start the rotation barely, not while the door is stopped", that is, "the force to rotate the door", the door is rotated, In the range of (i) to the above, "the force to rotate the door" and "the force to make the door close to the door by denting the latch" are added. Is divided into two so that different forces are applied to the door in each range so that an excessive force is not applied to the door.
The first problem to be solved by the invention is “how to make the“ force acting on the door ”different in each distinct range”.

Even if a different force is applied in each of the distinguished ranges, even if the “force acting on the door” is small in the “(A) range” described above, the rotation speed of the door continues as long as the force continues to act. Continues to increase, and further increases when a large force is applied in the above-mentioned “range (ii)”. The door is accelerating, and at least at the end of the above “(A) range” or at the beginning of the above “(A) range”, if the “means to decelerate the door” is not taken, the “spring The problem that “a moving door emits an impact sound when closed” cannot be solved.
When the door is closed from the fully opened position and when it is closed from the slightly opened position, the rotational speed of the door at the time of closing is different, and the magnitude of the inertial force attached to the door is also different. If the inertial force is large and the “means to decelerate the door” is weak, the brake will not work at all. If the inertial force is small and the “means for decelerating the door” is strong, the brake will be effective and stop the door. Thus, part 2 of the problem to be solved by the invention is “how to decelerate the door before the door closes”.

The door of the present invention is rotated at the end of “(A) range” or at the beginning of the above “(A) range” with “power enough to rotate the door”, and “decelerates the door” Taking the “means to do” means that the force acting on the door is less than or equal to the force that rotates the door, and it remains stopped before the door closes. According to the present invention, even if the door stops, the opening / closing device continues to operate and presses the door against the door so that the door is sealed. Part 3 of the problem to be solved by the invention is “before the door closes”. “Even if the force acting on the door” is small, how can the door be sealed with a small force?

If the door is rotated with such a small force and no extra force is applied at the time of sealing, the door rotates slowly and is gently unsealed. The door closer of the present invention does not feel heavy when the door is opened like the “door closer provided with a hydraulic cylinder” which is widely used.
However, the “door closer with a hydraulic cylinder” has a strong braking force, and has a function of responding to any door and closing slowly even when struck by a strong wind. The fourth problem to be solved by the invention is how the closing device of the present invention is provided with a function exceeding "a door closer with a hydraulic cylinder", and is generally spread. .

“Means to prevent the generation of a loud impact sound when closing” means that the “moment M of the force acting around the pivot axis O of the door in the“ the range of rotation of the door before the operation of pressing the door against the door (a) ”is performed. The size is smaller than “the magnitude of the moment M of force necessary to press the door against the door” and larger than the maximum static frictional force of the door. Regardless of the position at which the door is opened, the door that starts to rotate by a rotational force that is similar to the “maximum static frictional force acting around the pivot axis of the door” and that is larger than that rotates slowly.
“A spring that rotates the door by connecting one fulcrum to the support shaft provided on the door and the other fulcrum to the support shaft provided on the door frame or the surrounding wall surface. By providing on the door or door frame near the pivot axis or on the wall surface around it, and by providing the pivot connecting the other fulcrum on the door or door frame or the surrounding wall surface located far from the pivot axis of the door Rotation control of the door characterized in that the distance between the line of action of the spring force and the pivot of the door is reduced, and the expansion and contraction of the spring accompanying the rotation of the door is reduced to reduce the acceleration of the rotation of the door. mechanism."

Such “means for preventing the generation of a loud impact sound when closed” is not limited to “a door whose rotating shaft is vertical”, but is a technology that extends to the other opening / closing body and further to the moving body. Solve various problems.
“Means to prevent the door from making a loud impact noise” means that the magnitude of the acting force differs between the working range and the non-working range. This is a rotation mechanism that divides the rotation range into two parts and allows different forces to act in each of the distinguished rotation ranges. Such a rotation mechanism is recognized not only in doors but also in other industrial fields. A feature of the rotation mechanism of the present invention is a mechanism in which there is a clear boundary between different ranges, and the magnitude of the force changes from large to small or small to large at the boundary. It is that the magnitude of the force acting on the rotating body is different at the boundary. The rotation mechanism is
“With two reciprocating movements of two open / close bodies that rotate relative to each other and two movable bodies that face each other along one path and move away from each other, do not work. It is a means for dividing so that the magnitude of the force acting in each range is different, and the magnitude of the force at the boundary between the two ranges depends on the movement of the point of action of the force or the line of action of the force The rotation control mechanism or the movement control mechanism is characterized in that the “distance between the rotation shaft and the line of action of the force” is switched from L large to small or small to large by changing the direction of the rotation. And

"" A rotation control mechanism in which the rotating body D rotates by the force F acting around the rotation axis O, the rotation force M acting around the rotation axis O, the rotation axis O, and the line of action of the force F This is a rotation control mechanism in which the magnitude of the rotational force M or the force F is changed by changing the magnitude of the distance L according to the relationship (M = F × L) established with the distance L between the two. And
Rotating the rotating body D with a small force by reducing the rotational force M by decreasing the distance L, or decreasing the force F by increasing the distance L. Rotating means ”, the rotational force M is increased by increasing the distance L, or the force F is increased by decreasing the distance L, and the rotating body D is rotated with a large force. “Rotating means in the range of (ii)” and “Rotating means in the range of (a)” to “Rotating means in the range of (ii)” or “Rotating means in the range of (ii)” to “(A ) A rotation control mechanism comprising a "switching means" for switching to a "rotating means in the range", wherein the "switching means" involves no or little rotation of the rotating body D. mechanism. ""

A "releasable restraining means" that restricts the movement or rotation of the line of action of the force F to be small, and the expansion / contraction section has a "switching means" that operates largely with a predetermined opening of the rotating body as a boundary It is characterized by. However, the rotation mechanism in which the distance L is zero is not included.
The magnitude of the force at the boundary between the two ranges is switched from large to small or from small to large by moving the point of action of the force or by changing the direction of the line of action of the force. During the conversion, the magnitude of the force is switched with little or no rotation or movement of the rotating body. (Hereinafter, the sliding surface K means the sliding surface K or a cam body having the sliding surface K, and the door frame W means the door frame and the surrounding wall surface.)
In the “switching means”, the action point of the action line of the force F rotates as shown in FIGS. 13, 4 and 35, and the radius of rotation changes, and the force F as shown in FIGS. In any case, the action line of the force F moves and the “distance L between the rotation axis and the action line of the force” changes, and each of the rotating bodies is changed. The force acting on the rotating body is different in the rotation range (for example, “(A) range”, “(I) range”).
The first means for making the force acting on the rotating body different in the respective rotating ranges (“(A) range”, “(I) range”) of the rotating body is shown in FIGS. , 56, the line of action of force F rotates around the point of action, and the point of action of force F is transferred. A "rotating device" for rotating the rotating body and a "sealing device" for rotating the rotating body at a distance, and "rotating means in the range of (i)", and from the "rotating device" to the "sealing device" Or “switching means” for switching from “sealing device” to “rotating device”. ”“ Rotating device ”and“ sealing device ”function as well as function time Different.

The movement of the rotation control mechanism can be reversed, and there is a thing different from the same movement when closing when opening (for example, the former is FIGS. 1, 9, 34 to 37, and the latter is 3 to 6). Even at the time of closing, the rotation control mechanism performs one fixed movement and the “switching means” is executed, the movement before the “switching means” is executed, and the movement after the execution. There are some that are different.
The rotation control mechanism shown in FIGS. 34 to 37 repeats one fixed motion, and the cam wheel B is in the middle part of the cam body sliding surface K, restrains the distance L small, and releases the restraint at the end. The distance L is increased. At the boundary where the distance L is switched, the force action line rotates greatly and changes its direction. Further, the cam wheel B is small before the relative rotation of the cam body sliding surface K is switched and is large after that. The embodiment shown in FIGS. 34 to 37 includes “releasable restraining means” and “switching means”. The rotation control mechanisms of FIGS. 3 to 7 have different movements before and after the “switching means” are executed, and the movements are different between when the “restraining means” is effective and when it is released. The point of action of the force is greatly moved by the “switching means”.

As shown in FIGS. 2 to 5, FIGS. 28 to 30, and FIGS. 67 to 70, for example, the structure of the opening / closing apparatus having the rotation control mechanism is “relatively facing each other about a common rotation axis O. Structure 1 with rotating fixed part W and rotating body D. "
In FIG. 3, the fixed portion W is a door frame W having a fixed support shaft Sw, the rotating body D is the door D, and the common rotating shaft O is the door pivot O. For example, the two blades of the scissors shown in FIG. 94 have many blades on one side, which are fixed portions W not shown in the drawing, and the other blade is a door D. Examples applied to other industrial fields are shown in FIGS. 47 and 48, FIGS. 53 to 55, and FIGS.
As shown in FIG. 6 and FIGS. 23 to 27, for example, the opening / closing device 2 provided with the rotation control mechanism is as follows.
“Structure in which two rotating bodies that are separated from each other rotate by a force acting around a pair of rotating shafts, part 2”
Structure 3 including the rotation control mechanism is “a structure in which an expansion / contraction part is attached between two opening / closing bodies or two moving bodies, and two moving bodies that face each other along one path and approach or separate from each other”. And
For example, as shown in FIGS.
“The fixed shaft Sw provided with the rotating body D, the fixed portion W provided with the rotating shaft O, and the connecting shaft C provided with one end portion on the rotating body D and the other end portion provided with the fixed portion W. An opening / closing device 3 with which the rotating body D and the fixed portion W rotate relative to each other when the expanding / contracting portion expands / contracts.
Assuming that the rotating body D and the fixed portion W rotate relatively, FIGS. 3 and 4 are the same. For example, in FIGS. 3-5, the said expansion-contraction part is comprised with a spring. For example, in FIGS. 7-22, the said expansion-contraction part is comprised by one or more links.

Structure 1 is, for example, a simple rotation control mechanism of the present invention shown in FIG.
“A plate spring having a fixed shaft and a movable shaft attached to both ends, and a pair of rotating bodies that are connected to each other and share a single rotating shaft, and rotate relative to each other. An open / close device in which a fixed shaft is connected, a groove is provided on the other side, and the movable shaft is movably attached along the groove,
The groove is a passage that continues from the position of the rotary shaft or a position far from the position, and the movable shaft is close to the rotary shaft of the passage at a predetermined opening degree of the pair of rotating bodies. An opening / closing mechanism comprising a “switching means” that moves to a position far from or from a far position to a near position. "
As shown in FIG. 67, the spring employed in the urging means of the rotating body is a means in which one end of the spring is stopped at a different position so that forces of different magnitudes are applied in different rotation ranges. However, the case where the distance L is zero is included.

Structure 2 is, for example, a rotating mechanism including a cam body sliding surface shown in FIGS. 34 to 37 and a cam wheel that moves along with the sliding surface.
A rotating device in which a rotating body that is separated from each other is rotated by a force acting around a pair of rotating shafts, the cam wheel rotating body Jq rotating around the cam wheel rotating body rotating shaft Qj and the cam body rotating shaft A cam body KK that rotates about Qk as an axis, and a sliding surface K provided on the cam body KK presses the cam wheel B mounted on the tip of the cam wheel rotating body Jq to rotate the cam wheel rotating body Jq. Device,
When the cam wheel B is in the middle of the sliding surface K, the distance between the line of action T of the force by which the sliding surface K presses the cam wheel B and the cam wheel rotating body rotation axis Qj is small. The "rotating means in the range of (A)" and the cam wheel B rotate at the end of the sliding surface K so that the force action line T rotates and the force action line T and the cam wheel rotating body. Rotation in which a rotary member that is separated from each other by a force acting around a pair of rotary shafts or an opening / closing device provided with “rotating means in the range of (ii)” in which the distance between the rotary shafts Qj is largely switched The apparatus includes a cam wheel rotating body Jq that rotates about the cam wheel rotating body rotation axis Qj and a cam body KK that rotates about the cam body rotating shaft Qk. This is a rotating device that rotates the cam wheel rotor Jq by pressing the cam wheel B attached to the tip of the cam wheel rotor Jq. The sliding surface K is continuous to a position far from the position close to the pivot O in the vicinity of the pivot O, and the “releasable restraining means” that keeps the cam wheel B in the vicinity of the pivot O in the vicinity of the pivot O; “Switching means” for moving the moving support shaft to a position far from the rotation shaft is provided.

Opening and closing device 3 provided with the rotation control mechanism,
"In the reciprocating motion of two opening / closing bodies that share a rotation axis and rotate relative to each other, and two moving bodies that face each other along one path and approach or separate from each other, the two ranges The magnitude of the force at the boundary is a means of switching from large to small or from small to large by moving the point of action of the force or by changing the direction of the line of action of the force,
The rotation mechanism has a structure in which an expansion / contraction part is attached between two opening / closing bodies or two moving bodies. When the expansion / contraction part expands / contracts, “when two opening / closing bodies or two moving bodies and the expansion / contraction part are attached, The “attachment shaft” is moved along a circular orbit for the two opening / closing bodies, and is moved along a linear orbit for the two moving bodies as shown in FIG. 90, for example. The trajectory may be a circle, a straight line, or an arbitrary shape as long as it is a predetermined trajectory.
The rotating mechanism is related to two rotating bodies that rotate by transmitting force to each other around a pair of rotating shafts. The opening / closing device is an opening / closing body D that rotates about a pivot O provided in a fixed portion W. The connecting shaft C provided on the opening / closing body D and the fixed support shaft Sw provided on the fixed portion W are connected by an urging means, and the urging means is connected between the connection shaft C and the fixed support shaft Sw. It is an elastic member that changes the distance between them.

““ The rotating body, the fixed portion for providing the rotating shaft, the telescopic portion having one end portion close to the rotating shaft and the other end portion distant from the rotating shaft, and the position distant from the rotating shaft A fixed support shaft Sw provided in the fixed portion or a connecting shaft C provided in the rotating body at a position far from the rotating shaft, and a passage continuing from the position of the rotating shaft or a position far from the close position. A moving support shaft that moves along the passage,
The one end is the moving support shaft, and the other end is the fixed support shaft Sw when the passage is provided in the rotating body, and the connection shaft when the passage is provided in the fixed portion. A rotation control mechanism that is connected to C and rotates the rotating body by changing the length between one end and the other end;
When the moving support shaft is at or near the rotational shaft, the rotating body is rotated with a small force, and when the moving support shaft is at a position far from the rotating shaft, the rotating body is rotated with a large force or invalid with respect to the rotating body. A rotation control mechanism that works to
A "releasable restraining means" for stopping the moving support shaft at or near a position of the rotating shaft; and a "switching means" for moving the moving support shaft to a position far from the rotating shaft. Rotation control mechanism "
A rotating mechanism characterized in that the rotating mechanism is movably attached to a position far from the center. "
The “passage continuing from the position of the rotation axis or a position far from the position” includes “releasable restraining means”. One of the mounting shaft for mounting the urging means and the connecting shaft C and the mounting shaft for mounting the urging means and the fixed support shaft Sw is close to the pivot O, and the other is far from the pivot O. One of the above mounting shafts is an opening / closing device that is movably attached to a position far from the pivot O, and one of the mounting shafts is held at a position near the pivot O. “Rotating means”, “rotating means in the range of (i)” moving away from the pivot axis O, and switching the distance between one of the mounting shafts and the pivot axis O from small to large, or from large to small “ It is characterized by comprising "switching means".

One of the attachment shaft for attaching the urging means and the connecting shaft C and the attachment shaft for attaching the urging means and the fixed support shaft Sw are located close to the pivot axis O, and the other is located far away. The former will be referred to as the near mounting shaft and the latter as the far mounting shaft.
3 and 4, the opening / closing body D is a door D that rotates about the pivot axis O of the door, and the urging means is a pulling spring V and a link A, and is located near the pivot O in FIG. Is an embodiment in which the urging means and the fixed support shaft Sw are attached, and FIG. 4 is an embodiment in which the urging means and the connecting shaft C are attached.
The near attachment shaft is movably attached from a position near the pivot O to a position far from the pivot O, and in the vicinity of the pivot O, a passage (hereinafter referred to as a near passage) continuous from a position near to the pivot O is provided. In FIGS. 3 and 4, the adjacent mounting shaft that is mounted so as to be movable is a moving support shaft Sj that is provided at the tip of the link A and connects the pulling spring V, and the adjacent passage is a circular track of the moving support shaft Sj. . In FIG. 6, the vicinity mounting shaft is a wheel B, and the vicinity passage is a sliding surface K that continues from a position near to the pivot axis O to a position far from it. FIG. 6 shows an embodiment in which the adjacent passage is attached to the door frame W.
However, FIGS. 35 and 81 show the case where the adjacent passage is not provided with a releasable restraining means, and there is no movement of the action point, but the action line rotates and the distance from the rotation axis is increased from small to large, or Switch from large to small

FIG. 20 shows an embodiment in which the adjacent passage is attached to the door D.
The passage is provided with a releasable restraining means, and the restraining means is also a “rotating means in the range (A)” that keeps the adjacent mounting shaft in a position close to the pivot axis O, and is moved away from the pivot axis O. It is also a means for moving the action line of the force acting on the adjacent mounting shaft, and in a broad sense, the distance between the action line of the force acting around the rotation axis and the rotation axis. “Switching means” for switching from small to large or from large to small is provided.
3 and 4, the distance Lv between the rotation line O and the action line Fv of the force acting around the rotation axis O together with the link A rotating away from the contact Gj is switched from small to large. In FIG. 20, the wheel B moves along the sliding surface K and moves away from the pivot axis O, thereby starting the sealing device provided at a position near the pivot axis O. That is, the point of action of the force acting on the door moves discontinuously.

In the present invention, the operation is inherited from the rotating work to the sealing work, and most of the rotating work and the sealing work are processed by one apparatus. However, as shown in FIG. It is relayed from the rotating device involved to the sealing device engaged in the latter operation. That is,
“The rotating means in the range“ (a) ”is a rotating device that rotates the rotating body with the point of application of the force F close to the rotation axis, and the“ rotating means in the range (ii) ”. The rotation control mechanism according to claim 1, which is a hermetically sealed device that rotates the rotating body with the point of action of the force F being far away. "

The opening / closing device of the present invention is a link device including a rotating body, a fixed portion, and a plurality of links, and both the rotating body and the fixed portion are one of the links constituting the link device.
“A link including a fixed portion, a rotating body that rotates about a rotation shaft provided in the fixed portion, and a plurality of links that connect a support shaft provided in the fixed portion and a connection shaft provided in the rotating body. An apparatus comprising a releasable restraining means for restraining rotation of one of the fixed portion, the rotating body, and the plurality of links,
The link device includes a "rotating means in the range (A)" that rotates by restricting the rotation, a "rotating means in the range (I)" that rotates by releasing the rotational restriction, and the rotating body. An opening / closing apparatus comprising a "switching means" in which the restraining means works from invalid to valid or valid to invalid at a predetermined opening.
The wheel BB in FIG. 20 and the rotating body Jc in FIG. 50 are provided with releasable restraining means. Another embodiment of the structure of FIG. 4 is a link device that connects the rotating body (D) and the fixed portion (W) with a plurality of links (J, A, AA) in FIGS. Each of the two adjacent links (A, J) constituting the link device is provided with a contact portion (G) that contacts and separates from each other by the rotation of the rotating body. Each of the two matching links (D, Jc) is relatively integrated.
In the opening / closing device having the releasable restraining means, the link device has a contact where the fixed portion, the rotating body, and the plurality of links are engaged and disengaged, The above-mentioned releasable restraining means that works effectively and leaves and works invalidly,
Alternatively, a groove is provided on one side of the fixed portion, the rotating body, and the plurality of links, and a slider that moves along the groove is mounted on the other side. The opening / closing apparatus comprising the releasable restraining means that swings between a working position and an invalid working position.
In FIGS. 10 to 12, a groove is provided on any one of the adjacent connecting portions other than the “connecting portion with the door or door frame”, and a slider that moves along the groove is mounted on the other. Generally, it is “an opening / closing device in which one of the two adjacent links constituting the link device is the rotating body or the fixed portion.” FIG. 12 shows the rotating body (D) and the fixed portion (W ) Are two links (J, A,).
The trajectory along which the connecting shaft that connects the adjacent links moves is a passage that continues from a position close to the rotating shaft to a position far from the rotating shaft.
“A link including a fixed portion, a rotating body that rotates about a rotation shaft provided in the fixed portion, and a plurality of links that connect a support shaft provided in the fixed portion and a connection shaft provided in the rotating body. A connecting shaft provided at an end of any one of the fixed portion, the rotating body, and the plurality of links moves along a path that is continuous from a position close to the rotating shaft to a position far from the rotating shaft; An opening / closing device comprising releasable restraining means for stopping the shaft at a position close to the rotation shaft.
In the case where the connecting shaft connecting the links revolves and the passage is a circular orbit, FIGS. 3, 4, 53 and 65 involve rotation of the action line. 50, 108, and 109, the connecting shaft moves far and the force does not act. In the case where the slider attached to the connecting shaft moves along the passage, and the passage has a substantially straight track, the force acts near the rotating shaft in FIGS. Will not work. 6, 7, 45, 47, 57 to 60, 114, and 115, the action point moves along the path from the vicinity of the rotation axis to the distance. 67, 70 and 94 are composed of a biasing means with one spring and a passage through which one end of the spring moves. 88, 90, and 92, the action point does not move along the passage.
3-5, 14-18, 28-33, 57-73, 59, 60
"Opening / closing device in which a spring (V) is attached in place of one of the links constituting the link device."
In FIG. 59, “one of the plurality of links and one of the fixed portions is provided with a sliding surface, and the other is moved along the sliding surface, and the wheel and the sliding surface are separated. An opening and closing device characterized by engaging. "
In FIG. 59, the link A functions as a lever only immediately before the door is closed.
In FIG. 76, “the rotating means in the range (A) where the acting body moves around the wheel or the sliding surface with little rotation” and “the rotating means in the (A) range” that moves while rotating largely. Prepare.
In FIG. 44, it does not lead to sealing. In FIG. 72, when the door is closed, it works as a sealing device, and when the door is opened, the device is returned.

For example, the “opening / closing device that connects the fixed portion and the fixed portion to two links” shown in FIGS. 61 to 64 does not include the releasable restraining means. That is,
“A link including a fixed portion, a rotating body that rotates about a rotation shaft provided in the fixed portion, and two links that connect a support shaft provided in the fixed portion and a connection shaft provided in the rotating body. An opening and closing device comprising a device and a door stop that contacts the rotating body and prevents one rotation of the rotating body,
The link device moves in a state where the axis cores of the two links are not arranged in a straight line and “the rotation means in the range (A)” and the axis cores of the two links are arranged in a substantially straight line. “Rotating means in the range of (ii)” and the state where the axial cores of the two links are not arranged on a straight line, or are switched from a state arranged on a straight line to a state where they are not arranged. With "switching means"
An opening / closing device in which the rotating body is strongly pressed against a door when the axial cores of the two links are arranged on a straight line. "
61 and 62, the axis lines of the two links overlap, and in the apparatus shown in FIGS. 63 and 64, the doors intersecting the axis lines of the two links approach 180 degrees. In both cases, the axes of the two links are arranged in a straight line.

For example, the “means comprising a cam wheel and a cam body sliding surface” shown in FIGS. 34 to 37 and 79 to 82 has a feature that the force acting in the moving direction is small even if the force pressing the sliding surface is large. ,
“In an opening and closing device in which two rotating bodies that are separated from each other rotate by a force acting around a pair of rotating shafts, a sliding surface is provided on one of the two rotating bodies, and the other tip of the two rotating bodies is provided. The rotating shaft of the wheel is provided in the part, and the wheel mounted on the rotating shaft of the wheel moves along the sliding surface, so that the two rotating bodies rotate relatively, and the shape of the sliding surface is An opening / closing device characterized in that a normal line standing on the sliding surface maintains a substantially constant distance from one of the pair of rotating shafts. "
As shown in FIGS. 97 to 102, the opening / closing device includes a “cam wheel rotating body or cam body that supports a large force in the axial direction and rotates with a small force in the circumferential direction” and swings the lid up and down. It is also a moving device that moves heavy objects.
“Opening and closing device characterized in that the shape of the sliding surface of the cam body is an involute vortex line.”
As shown in FIGS. 80 and 100, the opening / closing device is also a moving device that swings the lid up and down or moves a heavy object.

For example, the sealing device shown in FIGS. 15 to 18, 57, 82 includes a “cam wheel rotating body that supports a large force in the axial direction and rotates with a small force in the circumferential direction”.
“A wheel is mounted on one side of the door and the door frame, and a sliding surface is mounted on the other side with or without a rotating body, and the wheel moves relative to the sliding surface by moving relative to the sliding surface. An opening and closing device having a sealing function for bringing the door into close contact with the door by a pressing force acting between the moving surface,
When the wheel or sliding surface revolves around a rotating shaft provided on one of the door and the door frame, the line of action of the pressing force approaches the rotating shaft, and the rotating body moves in the axial direction. An opening and closing device characterized by supporting a large force and rotating with a small circumferential force. "
15 and 57, the wheel B is mounted on the rotating body J pivotally supported by the door frame, and the sliding surface K is mounted on the door.
In FIG. 16, a wheel B is mounted on a rotating body J that is pivotally supported by a door. The sliding surface K is attached to the door frame.
In FIG. 82, a sliding surface is rotatably mounted on the door and slides around a wheel B provided also on the door frame.
For example, the sealing device shown in FIGS.
“Wheels are movably mounted on one side of the door and door frame, and sliding surfaces are attached to both or one side of the door and door frame.
A pressing force acts between the wheel and the sliding surface by moving substantially parallel to the door surface where the wheel is closed and along a sliding surface attached to both or one of the door and the door frame. An opening / closing device having a sealing function for bringing the door into close contact with the door by the pressing force,
The opening / closing device, wherein the pressing force is supported by fixing one of sliding surfaces attached to both the door and the door frame. "
19 moves along the sliding surface where the wheel is attached to the door frame, and FIGS. 21, 49, 50 and 114 are inserted between the sliding surfaces where the wheel is attached to both the door and door frame. Is done.
For example, the sealing device shown in FIGS. 46, 49, 50, 57, 82, 102, 106, 107, 114, 115 is
“Opening / closing device in which either the rotating body, the sliding surface attached to the door, or the sliding surface attached to both of the door frame is movably attached to the door or door frame.”
In FIG. 46, when the sliding surface moves along the door frame, the force acting on the door is dispersed.
In FIG. 50, when the sliding surface is movably mounted, the door can be easily opened when the closed door is opened.
In FIGS. 57 and 82, the sealing force gradually grows when the sliding surface is movably attached.
In FIG. 102, when the sliding surface is movably mounted, the apparatus operates only in one of the reciprocating directions.
106 and 107 change the inertial force attached to the door to the braking force when the sliding surface is movably attached.
114 and 115 release the sealing force after sealing by attaching the sliding surface so as to be movable.

6, 44, 63, 72, 78, 104-109 "rotation control mechanism that converts the inertial force that attaches to the door before the closing dimension into braking force"
“A fixed portion, a rotating body that rotates about a rotation shaft provided in the fixed portion, a moving portion that comes into contact with one of the fixed portion and the rotating body and is movable and attaches to the other, the fixed portion, and the above An opening / closing device that includes an expansion / contraction part that connects the rotation body, and the rotation body rotates when the expansion / contraction part expands and contracts
An opening / closing device characterized in that a braking force whose magnitude is changed by the movement of the moving part in contact with the one side is applied to the rotating body. "
6, 44, 63, 72, the rotating body Jc, the rotating body J4 in FIG. 78, the rotating body KK in FIG. 105, the link A and the sliding surface K in FIG. 106, and the rotating body J in FIG. Moving surface K, rotating body J2 and rotating body J3 in FIG. 108, rotating body J4 and rotating body J3 in FIG.
"Rotational control mechanism that converts the inertial force that attaches to the door just before closing to braking force" shown in FIGS.
“Opening and closing device, wherein the action line of the braking force approaches the rotating shaft, thereby reducing the action of the braking force to rotate the rotating body.”
112 and 113, the direction in which the "force Fb that the sliding surface K presses the wheel B" acts on the door is shifted in a direction perpendicular to the closed door surface and rotated in the direction in which the door opens by the restoring force of the spring. do not do.

Opening and closing device comprising a damper member for braking the switching operation

As shown in FIGS. 41 to 43, the door that makes it “lightly felt when opening the door” is a door with a small sealing force, and the latch device of the present invention is
"" Rotating body rotatably supported on a rotating support shaft provided on one of "the side surface of the door opposite to the door pivot" and "the door frame side surface facing it", and the sliding surface provided on the other side The rotating body rotates along the sliding surface while rotating the door in the opening / closing direction, and the force that prevents the door from rotating in the opening direction is A latch device supported by a shaft or an outer edge of the rotating body. "
The latching force that prevents the reverse rotation of the door is a force toward the rotation axis in the latch, and the portion that supports the latching force is supported by a large contact portion of the latch rotation shaft or the outer edge of the latch.

The door described in FIGS. 85 to 87 is a door that opens freely until it is fully opened when the closed door is opened a little, and is closed automatically until it is fully closed when the door that is fully opened is slightly closed, and the position where the biasing direction is switched is Different doors when opening the door and closing the door. That is,
“A door that reciprocates between a fully open position and a fully closed position, and when the door is opened from the fully closed position, the door is urged in the fully open direction from the fully closed direction. An opening direction switching means for switching, and a closing direction switching means for switching from a state biased in the fully opened direction to a state biased in the fully closed direction when the door is closed from the fully opened position,
A door characterized in that the opening degree of the door when the opening direction switching means operates differs from the opening degree of the door when the closing direction switching means operates. "
As described below with reference to FIG. 85, the switching means provided in this door is “a rotating body that is rotatably supported around the rotating shaft of the rotating body and is urged by a toggle spring so as to reciprocate between two stationary positions. The rotating body moves from one of the stationary positions to the other at a position where the opening direction switching means operates and a position where the closing direction switching means operates.
“A rotating body that swings between a position that is urged by a toggle spring and is urged in the fully closed direction and a position that is urged in the fully opened direction and that is stationary in the fully opened direction, The rotating body is connected to the means for urging the door, and the rotator is attached to the door when switching from one of the state of being urged in the fully closing direction and the state of being urged in the fully opening direction. The above door in which the biasing direction of the biasing means is reversed. "
Switching means for switching freely by the rotation of the door, and by linking this to the opening / closing device of the present invention, the urging direction of the door is switched.

The first problem to be solved by the invention is solved by controlling the “distance between the line of action of force and the center of rotation”.
The rotational force M acting around the rotation axis is the product of the force F acting around the rotation axis and the distance L between the line of action of the force and the rotation axis, and the force F acting around the rotation axis is If they are the same, the rotational force M can be reduced by decreasing the distance L, and the rotational force M can be increased by increasing the distance L. The door that solves the first problem by controlling the "distance between the force line of action and the center of rotation"
“Rotating means in the range (A) that rotates the door while keeping the distance between the action line of the force acting around the door pivot and the door pivot small” and the action line of the force acting around the door pivot "Rotating means in the range (ii)" for rotating the door by increasing the distance between the door and the pivot of the door, and "Rotating means in the range (A)" or "Rotating means in the range (I)" A door provided with "switching means" that switches to Is.

For example, in FIG. 6, in the “range from fully open to just before closing (A)”, the wheel B stays in the vicinity of the door pivot O, and the distance between the line of action of the force acting around the door pivot and the door pivot. Is kept small and a small force continues to act on the door. In the “range from just before closing to the closing time (yes)”, the wheel B moves to a position far away from the door pivot O, and the distance between the line of action of the force acting around the door pivot and the door pivot is It grows and a big force acts on the door.
When the door is closed, the "straight line passing through the drive shaft C and the wheel rotation axis Ib", that is, the intersection angle between the axis of the link A and the sliding surface changes according to the rotation of the driven rotor, and the driven rotor The slider staying at a position close to the driven shaft O at the predetermined opening degree moves to a position far from the driven shaft.
When the door is closed, the “switching means” is switched from “the rotating means in the range (A)” to “the rotating means in the range (I)” and when the door is opened, the “switching means” is changed from “the rotating means in the range (I)” to “( A) driving shaft, driving rotating body, driven shaft and driven rotating body are general terms and are unified terms used in the present application.In Fig. 6, the connecting shaft C, the link A, and the pivot of the door. O and door D. Further, hereinafter, the axial center line means a straight line passing through the connecting shafts at both ends of the rigid body.

The embodiment of FIGS.
“In an opening / closing device provided with the above-mentioned door stop that prevents rotation of one of the driven rotating bodies, and a force is applied around the driven shaft to rotate the driven rotating body, a position near the driven shaft is applied to the force. A rotating device for rotating the driven rotating body and a sealing device for bringing the driven rotating body into close contact with the door stop using a position far from the driven shaft as an action point of force. An opening / closing device in which rotation transmission work is inherited from the sealing device or from the sealing device to the rotating device,
From the rotating device having a position close to the pivot axis O of the door in the “range from fully open to just before closing (A)”, the pivot axis of the door in “range from just before closing to the closing time (yes)” Although the rotation work is inherited by the sealing device having an action point far from O, both of these devices and the devices of the other embodiments keep the force action point close to the center of rotation. Suddenly at the boundary between “(A) range rotation means” and “(A) range rotation means” and “(A) range” and “(A) range” moving to a position far from the center of rotation. As a “switching means” that changes the position continuously or discontinuously to a position far from the center of rotation.

Alternatively, in the rotation mechanism that transmits the rotation of the drive rotator that rotates around the drive shaft to the driven rotator that rotates around the drive shaft, when the rotational force M acting around the drive shaft is the same, the above distance By increasing L, the force F is reduced to transmit the rotational force acting around the drive shaft to the driven rotating body, and by reducing the distance L, the force F is increased to increase the force around the drive shaft. Rotational force acting on the rotor can be greatly transmitted to the driven rotor. The opening / closing mechanism that solves the first problem by controlling the “distance between the force line of action and the center of rotation”
"In an opening / closing device in which a driven rotating body rotates around a driven shaft and rotates the driven rotating body, the" driven shaft is controlled by controlling the distance between the driven shaft and the line of action of the force ". An opening and closing device for rotating the body,
In the state where the distance between the driven shafts is kept small, “the rotating means in the range (A)” where “the force acting around the driven shaft” acts smallly, and in the state where the distance between the driven shafts is large, “Switching between“ Rotating means in the range of (ii) ”and“ Rotating means in the range of (A) ”or“ Rotating means of the range of (A) ”where the“ force acting around the driven shaft ”acts greatly A switchgear characterized by comprising:
Alternatively, in a switchgear in which an axial force is applied around the drive shaft by rotating the drive rotator, the “drive shaft is changed by changing the“ distance between the drive shafts and the line of action of the axial force ”. An opening / closing device that rotates the driven rotating body by controlling the “magnitude of the axial force acting around”, and the distance between the driving shafts is large, “the magnitude of the axial force acting around the driving shaft” "The rotating force in the range of (A)" where the "force acting around the driven shaft" acts small, while the distance between the driving shafts is small and "acts around the driving shaft" In the state where the “magnitude of the axial force” is large, “the rotating means in the range (ii)” and “the rotating means in the range (a)” in which the “force acting around the driven shaft” acts greatly or “Switching means” for switching to “Rotating means in the range of (A)” Switchgear for. Is.
Further, in distinction from the techniques of Patent Documents 14 to 17, in the “rotating means in the range (A)” and the “rotating means in the range (I)”, the biasing direction of the force acting around the driven shaft is It is a switchgear that does not reverse. The door is an opening / closing device in which the driven shaft is vertical.

For example, FIG. 13 shows an opening / closing device that pulls the door D through the swinging link AA by the rotation of the driving rotating body J with the fixed support shaft Sw as the driving shaft, but “range from fully open to immediately before closing ( A) ", the connecting shaft P rotates around the drive shaft with the rotation radius rp to pull the swing link AA, and the connecting shaft PP rotates in the" range from right before closing until closing ". The swing link AA is pulled by rotating around the drive shaft with the radius rpp. Since the rotation radius rpp is smaller than the rotation radius rp, the force pulling the swing link AA is larger at the rotation radius rpp.

The “rotating means in the range (A)” is similar to the “maximum static frictional force acting around the pivot axis of the door” regardless of the open position, and the door starts to rotate by a rotational force larger than that. It is what you want to do. The door that has started to rotate has a kinetic frictional force smaller than the maximum static frictional force around the pivot axis of the door, and the magnitude of the force acting on the door is excessive. The working air resistance is greatly affected, and the air resistance acting on the door and the force acting on the door are balanced. In this way, the door moves at a constant speed without acceleration. “Rotating means in the range of (A)” is a means that keeps the door exerting a force small enough not to keep the door stopped.

In the embodiment shown in FIG. 1, the door and the door frame are connected by the opening / closing device of the present invention, and one of the connecting shafts of the door and the opening / closing device is provided in the vicinity of the door pivot. Keeping the distance between the line of action of the "working force" and the door's pivot small, the force acting on the door is "a rotational force larger than the maximum static friction force working around the door's pivot" Try to keep on.

As shown in FIG. 1, when one end of the spring is provided in the vicinity of the pivot of the door and the other end is provided at a position far from the pivot of the door, the expansion and contraction of the spring is reduced. By reducing the amount of expansion and contraction of the spring, the decrease in the strain energy of the spring can be suppressed to a small extent, and the acceleration of the door can be suppressed to a small level. The acceleration of the door is a conversion of the strain energy of the spring, and the strength of the spring is not related to the acceleration of the door. The tension spring shown in FIG. 1 provides a strong sealing force by tightening strongly, and does not accelerate the door.

The open / close device shown in FIGS. 3 and 4 is composed of a link rotatably supported around a link support shaft, a driven rotating body rotatably supported around a driven shaft, and the driven shaft. A fixing portion for fixing, a moving support shaft is provided at an end of the link opposite to the link support shaft, a spring is connected to the moving support shaft, and the spring is connected to the opposite side of the moving support shaft. A structure in which a spring support shaft is provided at an end, and one of the link support shaft and the spring support shaft is attached to the fixed portion, and the other is attached to the driven rotating body,
An opening / closing device including a releasable restraining means that restrains the rotation of the link around the link support shaft and restrains the movement of the moving support shaft.

The opening / closing device shown in FIGS. 3 and 4 is configured to be able to move the “one mounting shaft of the spring provided in the vicinity of the door pivot” shown in FIG. The “mounting shaft” moves, and the “distance between the force line of action and the door pivot” increases.
FIG. 3 shows a structure in which the link support shaft is attached to the fixed portion and the spring support shaft is attached to the driven rotating body. FIG. It is a structure to be attached. The fixed part means a door frame or a wall surface in the vicinity thereof.

3 and 4 as well as in the case of FIGS.
The releasable restraining means is placed on the link to prevent the link from rotating in one direction around the link support shaft, and the movable support shaft is held at or near the position of the driven shaft. The spring is disengaged to enable rotation in the other direction so that the moving support shaft is separated from the vicinity of the driven shaft, and the spring is separated from a predetermined opening degree of the driven rotating body. By traversing the position of the link support shaft, the moving support shaft is separated from the vicinity of the driven shaft.
In the case of FIG. 15, the link support shaft is attached to the fixed portion, and the spring support shaft is attached to the driven rotating body, and the spring is provided around the link support shaft to prevent the link from rotating in one direction. Crossing the link rotates the link.

29 to 33, the releasable restraining means includes a wheel and a sliding surface that moves along the wheel, and the wheel and the sliding surface are located in the vicinity of the driven shaft. When the link is attached to the driven rotating body, one is attached to the link and the other is attached to the fixed part, and when the link is attached to the fixed part, one is attached to the link and the other is attached to the driven rotating body. Because
One of the driven rotating bodies revolves around the driven shaft while moving along the other by rotation of the driven rotating body, and the drive support shaft is moved to the driven shaft while the wheel is in contact with the sliding surface. The wheel is kept at a position or in the vicinity of the driven shaft so that the wheel is separated from the sliding surface at a predetermined opening degree of the driven rotating body and the driving support shaft is separated from the vicinity of the driven shaft. To do.
In FIGS. 29 to 31, the link is attached to the driven rotating body, and in FIGS. 29 and 30, the wheel is attached to the link and revolves around the driven shaft while moving along the sliding surface fixed to the fixing portion. In FIG. 31, the sliding surface is attached to the link and revolves around the driven shaft while moving along the wheel mounted on the fixing portion.
32 and 33, the link is attached to the fixed portion, and in FIG. 32, the wheel is attached to the link, and the sliding surface revolves around the driven shaft while moving along the sliding surface fixed to the driven rotating body. To do. In FIG. 31, the wheel revolves around the driven shaft while the sliding surface is attached to the link and moves along the wheel mounted on the driven rotating body.

2, 3 and 4 FIGS. 14 to 17 FIGS. 29 to 31 have an opening / closing device composed of a spring and a link. The link rotates even when the driven rotating body is stopped, and “force acting around the driven shaft” is generated. There is a feature that becomes larger. Just before the door closes, the spring force weakens, and there is no force to seal the door, and when the latch comes into contact with the door frame, the door will stop without being recessed, but the link device will still work Continue to seal.
The spring force is weakened just before closing, there is no force to close the door, and when the latch abuts the door frame, the latch does not dent before the latch abuts the door frame so that the door does not stop. It is necessary to largely switch the "force acting around the driven shaft", but in this case, "the door accelerates and emits an impact sound until the latch comes into contact with the door frame and comes into close contact with the door. This device can increase the “force acting around the driven shaft” after the latch comes into contact with the door frame and stops the door, and does not emit a large impact sound.

The rotation mechanism of the present invention attaches a closing device to “one mounting shaft provided in the vicinity of the door pivot” and “mounting shaft provided in a position far from the door pivot”. The distance between the action line of the “force acting around the door's pivot” and the door's pivot is increased by moving the “one mounting shaft provided on the door” away from the vicinity of the door's pivot, and “the force to rotate the door” And “force to rotate while closing the door” are set to different sizes.
The “distance between the line of action of force and the center of rotation” changes slightly even if the “connecting shaft provided at a position far from the pivot of the door” is moved, but “the connecting shaft provided near the pivot of the door” ”Is moved, the change is large.

A closing device to be attached to "" one attachment shaft provided in the vicinity of the driven shaft "and" the other attachment shaft provided at a position far from the driven shaft ", wherein the one attachment shaft and the other attachment shaft One is attached to the driven rotor and the other is attached to the fixed part.
The one mounting shaft is movably attached to the driven rotating body or fixed part, the position of the one mounting shaft is constrained to the vicinity of the driven shaft, and the restraint is released so that it can move to a position far from the driven shaft. A closing device with releasable restraining means to
When the driven rotating body is a door, by moving the "one mounting shaft provided near the door pivot" away from the vicinity of the door pivot, the action line of the "force acting around the door pivot" and the door pivot The distance is increased so that “the force to rotate the door” and “the force to rotate while closing the door” are different.
The opening / closing device of the present invention comprises a connecting shaft provided in the vicinity of the pivot of the door and a connecting shaft provided at a position far from the pivot of the door, and the former is movably attached to the door or door frame. Hereinafter, the attachment shaft of the driven rotating body to which the closing device is attached will be referred to as a connection shaft, and the attachment shaft of the fixed portion where the driven shaft is provided will be referred to as a fixed support shaft.

A link device is formed by attaching a driven rotating body and a fixed portion to two link members and attaching a closing device thereto.
Except for the “rotating mechanism of the drive unit including the cam wheel and the cam body sliding surface” described in FIG. 34, the rotating mechanism of the present invention is a link device mainly having four or more links, and is a driven rotating body. Since the (door) and the fixed portion (door frame) are two links, the driven rotating body (door) and the fixed portion (door frame) are connected by two or more links.
A link device composed of three links cannot form a stationary triangle, but when the door and the door frame are connected by a single link, for example, as shown in FIG. Link device consisting of three links will move when it is movably connected with a "slider that moves along"

In the link device having four or more links, the other two links other than the driven rotating body and the fixed portion are, for example, a driving rotating body (rotating body J) and an operating body (link) as illustrated in FIGS. A) is a crank mechanism that changes the rotation of the drive rotor to the reciprocating motion of the working body.
The releasable restraining means “slider moving along the groove” in FIG. 7 is provided, and the movement of the slider is restrained, restricted, or made free by the rotation of the driven rotating body. 50 is provided with a releasable restraining means “swinging link and contact”, and the contact is restrained, limited or freed by the rotation of the driven rotating body.
“Groove and slider” are generally unified terms, and in the embodiment shown in the present application, a wheel and a sliding surface, and the wheel means a slider that has little friction during movement.

As shown in FIG. 69, for example, the means for urging the action body includes a slider that moves along the groove, and there is a slider crank mechanism that changes the reciprocating motion of the action body into the rotation of the door. The link of the crank mechanism is composed of five links, and the link device of the slider crank mechanism reduces the number of links by one.
As the number of links constituting the link device increases, the movement of the device becomes free. For example, the link connecting axis must be restricted to move along the track. Providing such a track consists of five or more links because part of the force to be transmitted is supported by the track and not transmitted to the driven body, and the rotational resistance of the link connecting shaft increases. Link devices are not preferred. Further, it does not meet the gist of the present invention to make the spring force as small as possible.

The link device including three links shown in FIGS. 6 and 57 (f) includes a restraining means that can be attached and released so that the attachment shaft closer to the driven shaft can be moved. Generally speaking, it is an opening / closing device that transmits the rotation of a “drive rotator rotatably supported around a drive shaft” to a “driven rotator rotatably supported around a driven shaft”. A fixing portion for fixing the driven shaft; a sliding body provided on the driven rotating body or the fixing portion at a position close to the driven shaft; and a sliding surface provided on the sliding body. And a slider that moves along the
The slider is attached to a rotating shaft of a wheel provided at an end of the driving rotating body opposite to the driving shaft, and one of the sliding body and the driving shaft is attached to a fixed portion, and the other is the driven rotating body. For example, FIG. 6 shows that the sliding body is attached to the fixed part and the drive shaft is attached to the driven rotary body, and FIG. . The sliding surface is a passage from a position near to the driven shaft to a position far from the driven shaft so that the slider stays at a position near the driven shaft in the passage or moves to a position far from the driven shaft. A releasable restraining means to
The crossing angle between the “straight line passing through the drive shaft and the wheel rotation shaft” and the sliding surface changes due to the rotation of the driven shaft, and the above-mentioned covered opening is delimited by a predetermined opening degree of the driven rotating body. An opening / closing device characterized in that the slider staying at a position close to the driving shaft moves to a position far from the driven shaft.

The link device comprising four links shown in FIGS. 7 and 20 is provided with restraining means that can be attached and released so that the attachment shaft closer to the driven shaft can be moved.
In general,
An opening / closing device that transmits the rotation of a “drive rotator rotatably supported around a drive shaft” to a “driven rotator rotatably supported around a driven shaft”. A sliding portion provided on the driven rotating body or the fixed portion at a “position close to the driven shaft”, and a slider that moves along a sliding surface provided on the sliding body, With
The drive rotator is provided with a drive support shaft at an end opposite to the drive shaft, and an action body is rotatably connected around the drive support shaft. The slider is attached to the action body, and the slide One of the moving body and the driving shaft is attached to the fixed portion, and the other is attached to the driven rotating body, and the sliding surface is a passage from a position near to the driven shaft to a position far from the driven shaft, and the slider is A releasable restraining means for staying close to the driven shaft of the passage or moving to a position far along the passage;
The slider that stays at a position close to the driven shaft with a predetermined opening degree of the driven rotating body as a boundary when an angle of intersection between the axis of the acting body and the sliding surface changes due to rotation of the driven shaft. Is moved to a position far from the driven shaft.

For example, in FIG. 7, the sliding body is attached to the fixed portion, and the driving shaft is attached to the driven rotating body. In FIG. 20, the sliding body is attached to the driven rotating body, and the driving shaft is attached to the fixing portion.
In FIG. 7, the drive rotating body (rotating body J) is provided with a driving support shaft (connection shaft P) at the end opposite to the drive shaft (connection shaft C), so that it can rotate around the drive support shaft. The body (link A) is connected, the slider (wheel B) is mounted on the working body, one of the sliding body (sliding surface K) and the drive shaft is attached to the fixed portion, and the other is the driven rotation. Attach to the body.

The link device shown in FIG. 11 is a link device consisting of four links, similar to the link devices shown in FIGS. 7 and 20, and the far mounting shaft is movably attached to the driven shaft. The mounting shaft includes a releasable restraining means.
Even if the mounting shaft farther from the driven shaft moves, the “line of action of the force by which the slider presses the passage” remains far from the driven shaft as in the link device shown in FIGS. Although it does not move, it can be switched from a rotating device at a position near the driven shaft to a sealing device at a position far from the driven shaft. As a result, the “operation line from working around the driven shaft” moves to a position far from the driven shaft.

The link device shown in FIG. 12 is also a link device composed of four links, but the connecting shafts of the two links are movably attached, and the connecting shafts are provided with releasable restraining means. Also in this case, as a result, the “operation line from working around the driven shaft” is moved to a position far from the driven shaft.
As a conclusion, a link device composed of four links is provided if one of the connecting shafts of the links including the mounting shaft is movably mounted, and the connecting shaft includes a releasable restraining means. The action line from working around the driven shaft "moves to a position far from the driven shaft.

In general, the link device shown in FIGS.
An opening / closing device that transmits the rotation of a “drive rotator rotatably supported around a drive shaft” to a “driven rotator rotatably supported around a driven shaft”. The driving rotating body is provided with a driving support shaft at an end opposite to the driving shaft, and an operating body is rotatably connected around the driving support shaft. One of the drive shafts is connected to the fixed part and the other is connected to the driven rotating body,
A link device is configured by using the driven rotating body, the fixed portion, the driving rotating body, and the acting body as a link member, and one of the two link members connected to the connecting shaft of any one of the link devices. A slider is provided, and the other is provided with a slider that moves along a sliding surface provided in the slider.
The crossing angle of the shaft cores of the two links changes due to the rotation of the driven shaft, and at a predetermined opening degree of the driven rotating body, “the action line of the force acting around the driven shaft and the driven shaft”. A switchgear characterized in that the "distance from the drive shaft" is constrained to be small or increased by releasing the restraint.

Next, a link device that does not include a “sliding surface and a slider that moves along the sliding surface” will be described. There will be described a link device for connecting a drive shaft and a driven rotating body with three links and a link device for connecting with two links.
50 and 65 are link devices composed of five links, which are opening / closing devices that connect the drive shaft and the driven rotating body with three links. The releasable restraining means attached to the attachment shaft closer to the driven shaft includes the above-mentioned “means restraining by the sliding surface and the wheel moving along the above” and “link and abut against it” described below. The link is connected in place of the wheel mounted on the working support shaft provided at the tip of the working body in the former, and comes into contact with and separates from the link instead of the sliding surface. Prepare for winning.

In general,
An opening / closing device that transmits the rotation of a “drive rotator rotatably supported around a drive shaft” to a “driven rotator rotatably supported around a driven shaft”. And the action body is connected to the “drive support shaft provided at the end opposite to the drive shaft of the drive rotating body”, and “the end of the action body opposite to the drive support shaft” The swing support link is attached to the “acting support shaft provided in the section”,
A structure in which one of the drive shaft and the drive shaft is attached to the fixed portion and the other is attached to the driven rotating body. Around the "swing link and the working body," the "swing link and the working body are provided to prevent the swinging link from rotating in one direction and restrict the movement of the working support shaft or release the restraint to enable the movement." The crossing angle of the shaft core line "changes with the rotation of the driven shaft, and the movement of the working support shaft can be restricted or released at a predetermined opening degree of the driven rotating body. An opening and closing device characterized by that. "

For example, in FIG. 50, the link support shaft is attached to the driven rotary body and the drive shaft is attached to the fixed portion, and in FIG. 65, the link support shaft is attached to the fixed portion, and the drive shaft is attached to the driven rotary body. In FIG. 50, the action (link A) is connected to the drive support shaft (connection shaft P) provided at the end P opposite to the drive shaft (rotation body rotation axis Q) of the drive rotation body J, and swings on the action body. A link (rotating body Jc) is attached. In FIG. 50, the restraining means is attached to one side of the link support shaft and includes “rotating means in the range (A)” and “switching means”, and FIG. 65 is attached to both sides of the link support shaft in the range of “(A) range”. Rotating means ”,“ switching means ”, and“ rotating means in the range (ii) ”.

The link device shown in FIGS. 13, 38 to 40, 48, and 88 is similar to the link device shown in FIGS. 50 and 65, and is an opening / closing device that connects the drive shaft and the driven rotating body with three links. Thus, instead of being mounted around the mounting shaft closer to the driven shaft of the link device shown in FIGS. 50 and 65, a contact is provided between the driving rotating body and the operating body, and the driving rotating body and the operating mechanism are operated. When a restraining means that can be released so as to be disengaged from the body is provided, the link device shown in FIG. 13 is obtained.

In general,
An opening / closing device that transmits the rotation of a “drive rotator rotatably supported around a drive shaft” to a “driven rotator rotatably supported around a driven shaft”. And the action body is connected to the “drive support shaft provided at the end opposite to the drive shaft of the drive rotating body”, and “the end of the action body opposite to the drive support shaft” A swing link is mounted on the action support shaft provided in the section, and a structure is provided around the drive support shaft so that the contact that causes the drive rotating body and the action body to disengage from each other is provided. A structure in which one of the drive shaft and the drive shaft is attached to the fixed portion and the other is attached to the driven rotating body, The “intersection angle of the axis of the acting body” is changed by the rotation of the driven shaft, and the driven The boundary of a predetermined degree of opening of the rotating body, switchgear the driving rotating body and the working body and is characterized by changing the engagement or disengagement state. "

For example, in FIG. 13, the link support shaft is attached to the driven rotating body, the drive shaft is attached to the fixed portion, and in FIG. 88, the link support shaft is attached to the fixed portion, and the drive shaft is attached to the driven rotating body.
In FIG. 13, before the driving rotating body (rotating body J) and the operating body (link A) are engaged, the operating body (link A) and the swinging link (link AA) are in a straight line, and after the engaging is completed. The axis of the link A and the link AA is bent. 25 and 26, the opening / closing device is such that the rotational force provided by the drive unit is switched from small to large, and the rotational force provided by the drive unit is in a state where the drive rotary body and the action body are separated. The rotation is small, and the drive rotation body and the action body are engaged and rotated.
In addition, the “link support shaft provided at the end of the swing link” can freely move on a plane, and can pull a driven body that moves not only in a circular motion but also along an arbitrary trajectory. Generally speaking, “Instead of the driven rotating body, a driven body that reciprocates along an arbitrary track provided in the fixed portion is provided, and the link support shaft is connected to the driven body in FIG. For example, as shown in FIG. 88, the opening / closing device shown is applicable not only to a revolving door but also to a sliding door.

As shown in FIGS. 13 and 38 to 40, “in an opening / closing device that connects a drive shaft and a driven rotating body with three links, the working support shaft (connection shaft PP) is the driving shaft (rotating body). The switchgear characterized by traversing a straight line passing through the rotation axis Q) and the link support shaft "is a straight line passing through the drive shaft and the link support shaft before the link cores of the link A and the link AA are bent. Crossing (straight line Z in FIG. 38) “the distance between the drive shaft and the link support shaft” increases and rotates in the direction in which the door opens.
In this state, even if the door is rotated by the rotation of the closing device, there is a characteristic that it does not move even if a force is directly applied to the door. Stop. Therefore, accidents that stuff your fingers can be prevented.
However, this door rotates in the direction that the door opens just before closing, and there is an impact close to a collision, and it cannot be opened when the door is closed. FIGS. 13, 40, 83, and 84 show these drawbacks. It has been resolved.

In the embodiment shown in FIGS. 59.60 and 76, a lever is attached to one of the working body and the fixed portion of the "opening / closing device for connecting the driving shaft and the driven rotating body with three links", and the other. A lever sliding surface that disengages from the lever wheel or moves along the lever wheel is provided. It is.
In the “range from fully open to just before closing (A)”, the action body moves around the lever wheel or the lever sliding surface with little rotation, In the range (ii), the lever wheel moves while rotating around the lever wheel or the lever sliding surface, and when the lever is closed, the action body is a lever that uses the lever wheel or the lever sliding surface as a fulcrum. And the driven rotor is brought into close contact with the door.

Generally speaking, “in place of the hit, a lever wheel is attached to one of the working body and the fixing portion, and the lever slide is engaged with or disengaged from the lever wheel or moved along the lever wheel. A surface is provided, and the working body moves with little rotation around the lever wheel or the sliding surface of the lever, and “the rotating means within the range (a)”; From the "rotating means in the range (ii)" that moves while rotating around the lever sliding surface and from the "rotating means in the range (a)" to the "rotating means in the range (ii)" An opening / closing device comprising “switching means” for switching. "

59 and 60, the embodiment is provided with a wheel or a sliding surface at the intermediate portion of the above-mentioned working body, but the wheel or the sliding surface is attached to the tip of the working body and the wheel moving along the sliding surface body is intermediate. Even if it is in the part, the acting body acts as a lever. The wheel or the sliding surface becomes a lever for the lever only when the driven rotating body comes into close contact with the door stop.
Although there is no description of an embodiment in which the action support shaft moves by the rotation of the swing link and the action body acts as a lever, it is the same as the case where the wheel moves along the sliding surface as shown in FIG. In addition, if the end of the working body close to the pivot of the door moves greatly immediately before closing, the working body acts as a lever even when the working support shaft moves due to the rotation of the swing link.
In the embodiment of Fig. 59.60, the working body is not connected to the drive rotator. Since the end portion is rotated, the above-mentioned action body acts as a lever. The embodiment of FIG. 59.60 employs an urging means for increasing the spring force at the time of sealing, and the spring force acts small before the sealing.

The embodiment shown in FIG. 76 is an embodiment in which an action body connected to a drive rotator has a sliding surface, and the action body moves along a wheel mounted on a rotation axis Ib of a wheel provided in a fixed portion. The wheel and lever sliding surface are not disengaged and engaged, and the end lever sliding surface moves along the lever wheel. In the "(A) range", the link AA hardly pushes the wheel B, and the direction of the line of action of the value K or the like is directed to the pivot axis O of the door just before closing, and does not act at right angles to the door surface. So it does not function as a lever. The acting body acts as a lever only in the “range from just before closing to the time of closing”. In the case of Patent Documents 19 and 20, it acts as a lever by acting at right angles to the end door surface.

Next, the “opening / closing device that connects the drive shaft and the driven rotating body with two links” will be described. As shown in FIGS. 61 and 62, for example, as shown in FIGS. 61 and 62, an opening / closing device for connecting a driving shaft and a driven rotating body with two links and providing two different magnitudes of force is provided. Actuator coupled to “supported rotating body” and “driving shaft provided at the end of the driving rotor opposite to the driving shaft”, a fixing portion for fixing the driven shaft, and driven rotation A door stop that contacts the body and prevents one of the driven rotating bodies from rotating, and the rotation of the driving rotating body is "the driven rotating body that is rotatably supported around the driven shaft". A switchgear that tells
A structure in which an action support shaft is provided at an end of the action body opposite to the drive support shaft, one of the action support shaft and the drive shaft is attached to the fixed portion, and the other is attached to the driven rotating body, As the drive rotator approaches the door stop, the distance between the working support shaft and the drive shaft is reduced, and the axis of the drive rotator immediately before the drive rotator contacts the door stop. The axis of the actuating body approaches a state where it substantially overlaps, while the axis of the driving rotator and the axis of the actuating body are kept substantially overlapping, the driving rotator rotates and the driven rotator becomes An opening and closing device characterized by being closely attached to a door stop.

Or, for example, as shown in FIGS. 63 and 64, “a drive rotating body that is rotatably supported around a drive shaft” and “a drive support shaft provided at the end of the drive rotating body opposite to the drive shaft”. An actuating body to be coupled; a fixed portion that fixes the driven shaft; and a door stop that contacts the driven rotating body and prevents one of the driven rotating bodies from rotating. An opening and closing device for transmitting to the driven rotating body pivotally supported around the driven shaft,
A structure in which an action support shaft is provided at an end of the action body opposite to the drive support shaft, one of the action support shaft and the drive shaft is attached to the fixed portion, and the other is attached to the driven rotating body, And one of the working support shaft and the drive shaft is provided at a position near the driven shaft, and the other is provided at a position far from the driven shaft. An opening / closing device characterized in that an axial core line approaches a straight line and the driven rotating body is brought into close contact with the door stop.

61-64,
“Drive rotator (rotator J) rotatably supported around the drive shaft (fixed support shaft Sw or connection shaft C)” and “the end of the drive rotator opposite to the drive shaft” An actuating body (link A) connected to the “drive support shaft (connecting shaft P)”, a fixed portion (door frame W) for fixing the driven shaft (door pivot O), and the driven rotating body (door) D) and a door stop (not shown) that abuts against (D) and prevents rotation of one of the driven rotating bodies.
In “range from fully open to just before closing (A)”, in FIG. 61, the link A hardly rotates and the connecting shaft P stays in the vicinity of the door pivot O, and the force acting on the door is small. In FIG. 63, the rotating body J and the link A are kept bent, and the force acting on the door is small. In the “range from immediately before closing to the closing time (i)”, in FIG. 61, the link A rotates greatly, the connecting shaft P moves to a position far from the door pivot O, and the force acting on the door is small. In FIG. 63, the rotating body J and the link A suddenly bend from a bent state to become a straight line, and the force acting on the door increases.

In the state where the shaft core line of the driving rotating body and the shaft core line of the working body are substantially overlapped or in a state of approaching a straight line, the rotational force acting on the center of rotation is changed to an axial force in any case. In the rotation mechanism, the “distance between the line of action of the axial force and the center of rotation” is brought close to zero, so that the magnitude of the axial force approaches infinity. The door is sealed so that a large force is applied at the end of rotation.

As described above, in both FIG. 61 and FIG. 63, the magnitude of the “force acting on the door” is close to infinity with “rotating means in the range (A)” that maintains a constant state with a value close to zero. There is a “rotating means in the range of (i)”, there is a clear boundary between them, and there is a “switching means” in which the “force acting on the door” suddenly increases.

Next, the sealing means will be described. As shown in FIGS. 15 to 17, for example, as shown in FIGS. 15 to 17, the opening / closing device sealing means that provides two different magnitudes of force with an opening / closing device other than the opening / closing device that connects the drive shaft and the driven rotating body with two links. An opening / closing device that transmits the rotation of a “drive rotator rotatably supported around a drive shaft” to a “driven rotator rotatably supported around a driven shaft”. A fixed part to be fixed, a door stop that contacts the driven rotating body and prevents one of the driven rotating bodies from rotating, a wheel, a sliding surface that moves along the wheel, and a sliding body that includes the sliding surface And one of the wheel and the sliding body is attached to the drive rotating body, and the other is attached to the fixed portion, and the wheel moves along the sliding surface while the wheel moves the sliding surface. Press to press and bring the driven rotor into close contact with the door stop An apparatus, the direction of the line of action of force which is in close contact with the driven rotating body per the door opening and closing device which is a right angle substantially the axial line of the driven rotating body. "

FIG. 56 illustrates the sealing means. The sealing means includes the above-mentioned “means in which the axial cores of two adjacent links overlap or be in a straight line” and “means provided with a cam wheel and a cam body sliding surface”. There is.
In the former, a link is connected to a rotating body that rotates at the center of rotation, and in the latter, a cam wheel is attached to the rotating body that rotates at the center of rotation. As shown in FIG. 56, in any case, the rotation mechanism changes the rotational force acting at the center of rotation into the “force for sealing the door”, and the rotational force acting at the center of rotation and the “force for sealing the door”. Therefore, when the “distance between the action line of the force that seals the door and the center of rotation” approaches zero, the magnitude of the axial force approaches infinity. In the latter case, when the wheel inclines horizontally with respect to the climbing slope, the so-called wedge effect causes a large force to press the slope even if the force in the approach direction is small. In the embodiment shown in FIGS. 15 to 17, the “force for sealing the door” is supported by the axial force acting on the rotating body rotating at the center of rotation, and in the embodiment shown in FIG. 119, the shearing force acting on the shaft Sf. 11 and 22, in the embodiment shown in FIGS.

The angle between the axis of the "rotating body with the wheel attached to the tip" and the gradient of the sliding surface is approximately a right angle, and the closer the right angle is, the greater the "the axial force that seals the door" becomes infinite Get closer to. Also, the gentler the slope of the sliding surface with respect to the movement of the wheels, the faster the "power to seal the door" grows with less rotation of the door. However, the closer the angle is to a right angle and the gentler the sliding surface is, the more difficult it is to open the closed door.
When the door closes, while the door rotates slightly, the wheel moves along the sliding surface substantially parallel to the “closed door surface”, but when the door is opened, the wheel reciprocates on the same sliding surface. When the wheel moves slightly parallel to the “closed door surface” while the door rotates slightly, it is subject to great resistance. When opening the door, there is less resistance if the wheel is turned back while the door is rotating greatly. That is, the sliding surface is preferably substantially parallel to the “closed door surface” when sealed, and inclined to the “closed door surface” when the door is opened.
The embodiment of FIGS. 46 and 49 is such that the sliding surface rotates. When sealed, the slope of the sliding surface is parallel to the “closed door surface” and the above angle is substantially perpendicular, and as the door is opened, the sliding surface changes. It rotates and the said angle reduces, A wheel becomes easy to move along a sliding surface.

As illustrated in FIGS.
An opening / closing device that transmits the rotation of a “drive rotator rotatably supported around a drive shaft” to a “driven rotator rotatably supported around a driven shaft”. A fixed portion that fixes the door, a door stop that contacts the driven rotating body and prevents one of the driven rotating bodies from rotating, a wheel, a sliding surface that moves along the wheel, and a slide that includes the sliding surface. A moving body, wherein one of the wheel and the sliding body is attached to the driving rotary body, and the other is attached to the fixed portion, the wheel is moved along the sliding surface, and the driven rotating body is An opening / closing device that prevents the door from coming into close contact. "
In the embodiment shown in FIGS. 44 and 45, a function of preventing the sealing is added to the sealing function by attaching a wheel or a sliding surface to the driving rotating body.

The means for providing two different magnitudes of force include the “means for moving the line of action of the force acting on the door away from near the pivot of the door” described in the embodiment of FIG. “Means consisting of two links to disengage” described above or “Means for switching the rotation radius of the action point” described in the embodiment of FIG. 15 “The action point of the force acting on the door is far from the vicinity of the pivot axis of the door. In addition to “means for moving”, “means for making the force action line and the link core line bend in a straight line” described in the embodiment of FIG. 56, which will be described later, will be described later in the embodiment of FIG. “Means including cam wheels and cam body sliding surfaces”.

In this case, the connecting shaft moves in a direction perpendicular to the “closed door surface”. That is, a passage perpendicular to the “closed door surface” is provided in the vicinity of the pivot of the door.
Patent Document 12 moves the “other connecting shaft far from the door pivot” and provides a passage parallel to the “closed door surface” at a position far from the door pivot.

Further, in order to increase the distance between the action line of “force acting around the door pivot” and the door pivot, for example, as shown in FIG. 19, the action point of “force acting around the door pivot” is set from the door pivot. Try to move to a far away position. The opening / closing device in this case includes a “rotating device” that keeps the action point in the vicinity of the pivot of the door, and a “sealing device” that applies a force to the action point provided at a position far from the pivot of the door. . In this case, the switchgear includes one that processes “rotational work” and “rotary work” with one switchgear, and one that processes with two apparatuses. At the end of the “rotating means”, the mode is automatically switched to “rotating means in the range (ii)”. In this case, moving the “one connecting shaft near the door pivot” away from the door pivot makes the “rotating means in the range (A)” invalid, It becomes “switching means” that automatically switches to “rotating means”. The connecting shaft does not need to move in a direction perpendicular to the “closed door surface”. For example, as illustrated in FIG. 20, the passage provided near the pivot of the door is parallel to the “closed door surface”. But it ’s okay.

Immediately before closing, to process the "dynamic inertia force attached to the door", the force to rotate the door by bringing the distance between the action line of "the force acting around the door axis" and the door axis to zero near the door immediately before closing. Rotate only with dynamic inertia force. For example, as illustrated in FIG. 69, the door does not remain stopped no matter where the hand is opened after the door is opened. When the force for rotating the door is insufficient immediately before closing, there is no force for sealing the door, the rotation of the door is stopped, and the closing device is also stopped. For example, as illustrated in FIG. 57, the connecting shaft that connects the closing device and the door or the door frame is movably attached so that the closing device does not stop even if the rotation of the door stops.

Means for solving the first to fifth problems to be solved by the invention will be described in detail.
Part 1 of the means for solving the first problem is that "one end of the spring is connected to the connecting shaft provided on the door or the driven rotating body, and the other end is connected to the fixed support shaft provided on the door frame or the surrounding wall surface. A spring for rotating the door, wherein the connecting shaft is provided at a position close to the pivot of the door or the driven rolling shaft, and the fixed support shaft is provided at a position far from the pivot of the door or the driven shaft, or the connection FIG. 1 shows an embodiment in which a shaft is provided at a position far from the door pivot or driven shaft, and the fixed support shaft is provided at a position near the door pivot or driven rotary shaft. An embodiment shown in FIG. 27 will be described with reference to FIG.
The drive rotator is a cam wheel rotator Jq in FIG. 27, and the drive rotator is a rotator of a drive unit that is driven by a spring not only in the door but also in “other industrial fields unrelated to the door”. The drive shaft means its rotational axis. Further, the driven rotating body is a rotating body driven by a driving unit, and the driven shaft means the rotating shaft.
By keeping the distance between the line of action of the spring force and the pivot or driven shaft of the door small, the force acting on the door is small even if the spring force is large. “Change in strain energy when the spring expands and contracts” accelerates the door. The acceleration of the door is related to the amount of change in the strength of the spring, and the strength of the spring is not related. Therefore, if the amount of expansion and contraction of the spring is reduced, the door will not accelerate.

As shown in FIG. 73, the second part of the means for solving the first problem includes a string that provides a tensile force by expanding or contracting, or a string connected in series with a spring, and a pulley. One end of the string or the string connected in series with the spring is connected to a connection shaft provided on the door, and the other end is connected to a fixed support shaft provided on the door frame or the surrounding wall surface. And at least one of the fixed support shafts is provided at a position far from the pivot or driven shaft of the door, and the pulley is provided at a position near the pivot or driven shaft of the door. By keeping the distance between the pivot and the driven shaft small, the force acting on the door is small even if the spring force is large.
The string or the string connected in series with the spring moves along the pulley ", and the string is decelerated by flattening when it is caught in the pulley. Even if the pulley is fixed to the door frame so as to be rotatable as shown in FIG. 73 (a) or fixed to the door frame as shown in FIG. 73 (c), there is a deceleration effect. Even if it is fixed to the frame so as to be arbitrarily movable, the deceleration effect can be exhibited.
The "means that the string moves along the pulley" is a means that decelerates by applying a certain amount of resistance, and does not strengthen the spring so that it feels heavy when the door is opened.

Part 1 and part 2 of the means for solving the first problem are “rotating means in the range of (A)”, and the door sealed with the magnetic catch is “rotating means in the range of (i)” and “switching means” Even if it is not equipped with ", a door that can be rotated slowly and sealed tightly" can be realized simply by providing "rotating means in the range of (A)".
Since the spring has the property of expanding and contracting in an instant, all devices driven by the spring operate in an instant, so not only doors but also other industrial fields "spring driven devices" are equipped with braking means and buffer means It is necessary to slow down the operation. In a device that begins to pull the “driven body where the maximum static friction force works” by “a force that is close to the maximum static friction force and larger”, a slight resistance is observed in a general door closer driven by a strong spring. Demonstrate the effect of oil viscosity resistance and slow down the movement of the driven body. The driven body is a general term for objects that are moved by a spring not only in the door but also in “other industrial fields not related to the door”.
Fix one end of the “strand that provides tensile force by expanding or contracting, or the cord connected in series with the spring” and connect the other end to the driven body so that it can be moved. In the traction mechanism that pulls the driven body so that the `` string connected in series with the spring '' moves along the pulley, the `` the other end '' is not limited to rotational motion and linear motion, It is possible to move in orbit. The device driven by the “movement of the other end” can omit the mounting of the braking means and the buffering means. The greater the number of pulleys that move along the string, the longer the dry movement distance and the greater the resistance to slight door rotation.

Part 1 of the means for solving the second problem is "means provided with releasable restraining means for stopping the action line of the force acting on the door near the pivot of the door", and the action line of the force acting on the door is By rotating, the direction is changed, and as a result, the distance between the line of action of the force acting on the door and the pivot of the door is changed.
The means provided with “continuous body AV connecting spring V and link A” described in FIGS. 3 and 4 is such that the end of the spring near the pivot axis O is rotatably attached in FIG. . The description will be made using terms defined in the rotation mechanism in the door and “other industrial fields not related to the door”. Hereinafter, parentheses indicate terms used in the description of the drawings. 3 and 4 show that “a driving rotating body (link A) rotatably supported around a driving shaft (a fixed supporting shaft Sw in FIG. 3 and a connecting shaft C in FIG. 4) and a driven shaft ( A driven rotating body (door D) rotatably supported around a pivot axis (O) of the door, and a fixed portion (door frame W) for fixing the driven rotating body rotating shaft; Opening / closing device that transmits the rotation of the drive rotating shaft to the driven shaft, provided with a drive support shaft (moving support shaft) at the end opposite to the drive shaft of the drive rotating body, and connecting a spring to the drive support shaft A spring support shaft is provided at an end of the spring opposite to the drive support shaft, and one of the drive shaft and the spring support shaft is attached to the fixed portion, and the other is attached to the driven rotating body. A structure to which the rotation of the driven rotating body is prevented by rotation of the driven rotating body. Switchgear characterized in that it comprises a releasable restraining means for restraining the movement of the drive shaft. "

As shown in FIGS. 3 and 4, the rotating mechanism including the driven rotating body and the “continuous body in which the spring and the link are connected” includes a rotating mechanism in which the spring supporting shaft revolves around the moving supporting shaft. And FIG.
As shown in FIG. 14, there is a rotation mechanism in which the link revolves around the moving support shaft, and the “rotation mechanism in which the link support shaft revolves around the spring support shaft” shown in FIGS. The “rotation mechanism in which the spring support shaft revolves around the moving support shaft” is the same as the rotation mechanism shown in FIGS. 3 and 4 are embodiments in which the driven rotary body is a door D, and FIGS. 14 to 17 are embodiments in which the driven rotary body is a door D and the link is a rotary body J. Is an embodiment in which the driven rotating body is a rotating body J.

In each rotation mechanism, one of the link support shaft and the spring support shaft is attached to the fixed support shaft, and the other is attached to the connection shaft. Further, “a restraining means is provided that can contact the link and prevent the rotation of the link in one direction around the link support shaft and enables the rotation in the other direction away from the link, that is, a releasable restraining means.
In the “(A) range”, the link is biased to the position where it hits, and the moving support shaft is held at the position of the driven rotating body rotating shaft or at a position close to the driven rotating body rotating shaft. Therefore, the force of the spring does not act on the driven rotating body or works slightly. The link is urged to move away from the contact within the range of “(i)”, the moving support shaft is moved to a position far from the rotational axis of the driven rotating body, and the spring force acts on the driven rotating body greatly. . 14 to 17, the movement of the movable support shaft becomes a “switching unit” that starts a sealing operation.

The other releasable restraining means includes a sliding surface that is attached to a wheel in the vicinity of the moving support shaft and moves along the wheel, and the wheel comes into contact with the sliding surface so as to contact the moving support shaft. The shaft is held in the vicinity of the link support shaft so that the wheel is separated from the sliding surface and the moving support shaft is separated from the vicinity of the link support shaft. One is attached to the fixed part, and the other is attached to the link. Examples will be described with reference to FIGS.
3, 4, 14 to 17, and FIGS. 29 to 33, the link that has started to rotate after the restraint is released rotates regardless of whether or not the rotation of the driven rotating body is stopped. Subsequently, there is a feature of increasing the “distance between the axis of the spring and the rotational axis of the driven rotor”. The embodiment of FIG. 53 is an apparatus for gripping an egg with the rotational force of the driven rotating body, which can increase the gripping force to grip the egg without operating the driven rotating body and lift the egg without crushing it. It becomes possible. That is, the rotation mechanism is an effective means not only for doors but also for “other industrial fields not related to doors”.

An opening / closing device in which a substantially perpendicular passage is provided in the vicinity of the door pivot O on the closed door surface, for example, the opening / closing device shown in FIGS. 6, 7, and 20 has a passage substantially parallel to the closed door surface near the door pivot O. The opening / closing device to be provided, for example, the opening / closing device shown in FIG. 51 is an opening / closing device that keeps the position of the wheel close to the driven shaft and moves to a position far from the driven shaft. An opening and closing device characterized by a sliding surface that can move to a distant position when closed. These closing devices directly rotate the “drive rotator (link A in FIG. 6) (rotary body J in FIG. 7)” rotatably supported around the drive shaft (connection shaft C in FIG. 6). Alternatively, an opening / closing device that transmits to a “driven rotating body (door D) rotatably supported around a driven shaft (door pivot O)” via an action body (link A in FIG. 7),
A fixed portion (door frame W) for fixing the driven shaft; a sliding body (sliding surface K) provided on the driven rotating body or the fixed portion at a position close to the driven shaft; A slider (wheel B) that moves along a sliding surface provided on the sliding body, and "a driving support shaft (wheel rotating shaft Ib) provided at an end of the driving rotating body opposite to the driving shaft" The slider is mounted on the driving support shaft, or the operating body is connected to the driving support shaft, and the slider is mounted on the “acting support shaft provided on the end of the operating body opposite to the driving support shaft”. A structure in which one of the sliding body and the driving shaft is attached to the fixed portion, and the other is attached to the driven rotating body, and the sliding surface extends from a position close to the driven shaft to a position far from the driven shaft. Opening and closing device characterized by being a passage. "
Hereinafter, a member that transmits a force to the driven rotating body is referred to as an action body, and a support shaft provided at an end of the action body on the driven rotating body side is referred to as an action support shaft. A drive rotating body is attached to the support shaft and is a drive support shaft.

“The contact point between the slider and the sliding surface” is the driving support shaft of the driving rotating body or the operating support shaft of the operating body, and the operating point of the “acting force acting on the driven rotating body” is driven. By moving from a position close to the axis to a position far from the axis, the “magnitude of the force acting on the driven rotating body” is changed. That is, the magnitude of the force is changed by holding the drive shaft at a close position and moving it to a distant position when the drive shaft is closed.
6 and 7, the sliding body is the sliding surface K and is attached to the door frame W in the vicinity of the “fixed portion, that is, the pivot axis O of the door”, and the driving rotary body is the link A in FIG. In this case, it is the rotating body J, and the drive shaft is attached to a driven shaft, that is, a connecting shaft C provided on the door. In the case of FIG. 20, the sliding body is a sliding surface Kd and is attached to the door D in the vicinity of the “fixed portion, ie, the pivot axis O of the door”, and in FIG. It is attached to a rotating body rotation axis Q provided on the frame W.
The “slider or wheel” is attached to the rotating shaft Ib of the wheel of the link A in the case of FIG. The

"A hand with a releasable restraining means that stops the line of action of the force acting on the door near the pivot of the door" is a "means restrained by a sliding surface and wheels moving along it" The body is a link A that moves in the axial direction by a crank mechanism of a rotating body J that rotates around a rotation axis by a spring in the embodiment of FIG. 7, and moves along a straight path in the embodiment of FIG. A shaft Sf that reciprocates linearly by a slider link mechanism.
6, 7 and 19 show an embodiment in which the sliding surface is attached to a fixed portion, that is, a door frame W, and the driving support shaft is attached to the driven rotating body, that is, the door D. The driving support shaft is fixed to the fixed portion, that is, the door frame. FIG. 20 shows an embodiment in which the sliding surface is attached to the driven rotating body, that is, the door D.

The rotation angle of the driven rotating body changes the crossing angle between the axis of the working body and the sliding surface, and the crossing angle is a right angle to prevent the movement of the wheel or keep it small, or A releasable restraining means for increasing the movement of the wheel is provided. Here, the axis of the working body is a straight line passing through the support shafts at both ends of the working body regardless of the shape of the working body, and the wheels are in the “range (A)” and the crossing angle is a right angle. It stops on the side that does not exceed and stays in the vicinity of the pivot of the door, and in the “range (ii)”, the crossing angle moves to the side beyond the right angle and moves away from the pivot of the door.
6 and 7, the movement of the wheel is “switching means” and “rotating means in the range (ii)”. In FIGS. 19 to 21, “rotating means in the range (a)” and “switching means”. It is.
10 to 11 show an embodiment in which the working body operates on the side far from the pivot axis O of the door. In the embodiment of FIG. 10, the rotating body J rotates around the rotation axis C by a spring, and in the embodiment of FIG. In the rotating body J that moves in the axial direction by the link A that rotates around the rotation axis by the spring, the movement of the wheel is “switching means” and “rotating means in the range of (i)”.

49. The embodiment of FIG. 49 is described in claim 7, wherein a sliding body rotating shaft is provided on the driven rotating body or the fixed portion, and the sliding body is rotatably supported around the sliding body rotating shaft. 49. In FIG. 49, the long hole Hd, and in FIGS. 57 and 58.81, the sliding surface K or Kd is rotatably supported around the connection axis C provided on the door D. The elongate hole or sliding surface is a path through which the wheel B moves from a position close to the far axis O of the door to a position far from the door, and provides different rotational forces.

Another "means having a releasable restraining means for stopping the line of action of the force acting on the door near the pivot axis of the door" is "a means for restraining by the link and the abutment against it" In the embodiment of FIG. 50, the rotation of the “drive rotating body (rotating body J) rotatably supported around the driving shaft (rotating body rotating shaft Q)” is rotated around the “driven shaft (door pivot O). An opening / closing device that transmits to a driven rotary body (door D) that is rotatably supported by the motor, and includes a fixing portion that fixes the driven shaft, and includes an end opposite to the drive shaft of the drive rotary body The drive support shaft (connection shaft P) provided in the section is attached to the swing link (rotating body Jc), or the action body (link A) is connected to the drive support shaft. "The working support shaft (connection shaft Cj) provided at the end opposite to the drive support shaft" One of the swing shaft and the drive shaft is attached to the fixed portion, and the other is attached to the fixed portion. A releasable restraining means for restraining the one-way rotation of the swing link around the link support shaft on one side or both sides of the swing link with a structure to be attached to the drive rotor. A switchgear characterized by being provided.

The “support shaft provided at the end of the swing link opposite to the link support shaft” is the drive support shaft of the drive rotating body or the action support shaft of the acting body, and the action of “force acting on the driven rotating body” At this point, the movement of the point of action is constrained to keep the “magnitude of the force acting on the driven rotating body” constant, and the restraint is released to change the “magnitude of the force acting on the driven rotating body”. Yes.
The structure in which the oscillating link is mounted on the drive support shaft is a link device consisting of four rigid bodies. Attaching the restraining means to this is a "link device consisting of three rigid bodies", and the triangle is not deformed, so the restraining means is attached. I can't do that. 62 and 75, it functions to indicate the position where the releasable restraining means is attached to one side of the swing link.

In FIG. 50, the rotating body Jc is provided with restraining means on one side of the swing link by the swing link, and includes “rotating means in the range (A)” and “switching means”. In FIG. 65, the link AA is the swing link, and the restraining means is provided on both sides of the swing link, so that “rotation means in the range (A)”, “rotation means in the range (I)” and “switching means”. With.

50, 65 (a) and 65 (b), the rotating body rotating shaft Q of the rotating body J is attached to the door frame W of the fixed portion, and the connecting shaft C of the link support shaft is the door D of the driven rotating body. In the embodiment of the structure to be attached to the rotating mechanism, the rotating mechanism has “rotating means in the range (A)” and “switching means”. FIGS. 65 (c) and 65 (d) show an embodiment in which the link support shaft is attached to the fixed portion when the urging means is attached to the driven rotating body. A rotation mechanism having a rotation means in the range of
The hit is caused by the rotation of the driven rotating body so that it is engaged with the link to prevent the link from rotating in one direction around the link support shaft, and separated to allow rotation in the other direction.
The link is urged in the direction of the hit in the “(A) range” and the action support shaft is held in the vicinity of the pivot of the door, and the link is separated from the hit in the “(A) range”. The working support shaft is biased away from the pivot of the door.

In addition to the releasable restraining means that constitute the “switching means”, the role of “the wheel and the sliding surface that moves along the wheel” is the role of sealing the door and the role of blocking the sealing just before closing the arrow. . “A door stop that contacts the driven rotating body and prevents rotation of one of the driven rotating bodies, a wheel, and a sliding surface that moves along the wheel, and one of the wheel and the sliding surface is the above-mentioned For example, FIGS. 10 to 12, 14 to 18, 20 to 22, 44, 45, 70, and 71 are structures to be attached to the drive rotator. 19, 46, 49, 50, 57, 58 are structures that attach to the working body. Many of the former perform the sealing operation by moving the wheels in a circular motion and many of the latter in a linear motion.

“The wheel moves along the sliding surface and the driven rotating body rotates, or the driven rotating body moves the wheel along the sliding surface,” for example, FIGS. As shown, the sealing operation is performed at the time of closing and opening, and the rotating body J is reversely rotated at the time of opening rotation to return the apparatus.
Or, for example, as shown in FIGS. 44 and 45, “the wheel moves along the sliding surface to prevent the driven rotating body from coming into close contact with the door stop” or the wheel slides. An opening / closing device that presses a surface to bring the driven rotary body into close contact with the door stop, wherein the direction of the line of action of the force that makes the driven rotary body come into close contact with the door stop is the axis of the driven rotary body The switchgear according to any one of claims 5 and 6 to 11, wherein the switchgear is substantially at right angles. "

The opening / closing device according to claim 12, wherein the sliding surface is rotatably supported or movably attached. For example, as shown in FIG. Brake by energizing in the direction to open the door.
For example, as described below with reference to FIG. 85, when the sliding surface rotates or moves, for example, the door of FIGS.

In these switchgears, the drive shaft is at a position far from the driven shaft, and the third means for solving the second problem is "the means for the action point of the force acting on the door to move away from near the pivot of the door. Is.
"A force is applied to a position near the rotational axis of the driven rotating body to rotate the driven rotating body" (rotating means in the range (A)), and a force is applied to a position far from the rotational axis of the driven rotating body. A "switching means" for switching to "rotating means in the range of (ii)" and "rotating means in the range of (a)" or "rotating means in the range of (ii)". It is characterized by that. "

When the action body to which the wheel for sealing the door is attached is substantially perpendicular to the “closed door surface” when it is closed and matches the direction of the sealing force, the action body is sealed with a force acting in the axial direction of the action body. When the action body to which the wheel for sealing the door is closed is substantially parallel to the “closed door surface” at the time of closing and is orthogonal to the direction of the sealing force, the action body functions as a lever, Seal with force acting perpendicular to the axial direction.
When the operating body is substantially parallel to the “closed door surface” at the time of closing, the form of the device when closed is not greatly protruded from the “closed door surface”, and the device is compact. Can be stored.

The location where the spring is attached to the link device of the present invention is not limited to the periphery of the drive shaft, but is attached around the connecting shaft where the “angle between adjacent links” continues to increase or decrease.
As shown in FIG. 64, the connecting shaft of the link device has a connecting shaft in which the “angle between adjacent links” turns from increasing to decreasing, and the direction in which the force acts and the moving direction are opposite to each other There are connecting shafts that continue to increase or decrease.

“Opening / closing device in which, instead of the driving rotating body, a leaf spring, a coil spring that deforms in a curved manner, or an elastic body that is not a rigid body is rotatably supported or fixed around the driving shaft”. Are shown in FIGS. For example, in FIGS. 70 and 71, the link A in FIG. 6 and the rotating body J in FIG. 7 replace the leaf springs, respectively.

The drive means of the link device of the present invention is a crank mechanism that mainly transmits the rotation of the drive rotating body directly or changes the rotation into a linear motion via the action body, and is a drive support shaft, that is, “the action body of the above action body. The end portion on the side opposite to the working spindle rotates.
In addition to the crank mechanism, there is a reciprocating slider mechanism for changing the linear motion to the rotation of the door as shown in FIGS. 19, 59 and 60, and the drive support shaft reciprocates linearly.
As shown in FIGS. 59, 60, 68, and 69, the embodiment is provided with a drive means replacing the drive rotating body, and the drive means is a passage through which the end of the action body opposite to the action support shaft reciprocates. An opening / closing device that includes a passage body that is rotatably supported around the drive shaft or is fixed to the drive shaft. "

The passage body is fixed to the drive shaft in FIG. 19, and is rotatably supported around the drive shaft in FIG. The “passage that reciprocates the driving support shaft” provided in the passage body does not need to be a straight line as shown in FIG. 60 and may be arbitrary.
When the "rotating path where the working support shaft of the working body reciprocates" and "passage where the end opposite to the working support shaft of the working body reciprocates" is provided in the driven rotating body and the fixed part, the link length changes. In the case where the connecting shaft is provided with an expansion joint, the number of links that connect the driven rotating body and the fixed portion may be one.
68 and 69 show an embodiment in which an expansion joint is provided on the connecting shaft.

The drive means of the link device of the present invention is a means for moving the drive support shaft, and the drive support shaft may be freely moved. What is necessary is just to provide "the spring which connects a drive spindle and a drive shaft".
In the embodiment shown in FIGS. 59 and 60, since it is not necessary to restrain the movement of the “end portion far from the pivot axis of the door”, the “end portion on the opposite side of the action support shaft of the action body and the drive shaft” are not required. And a spring that connects the two.
"Switching device 1"
“Moving body (D) moving along a predetermined track (K in FIG. 92)”, a fixed portion (W) provided with the predetermined track (K), and a fixed support provided on the fixed portion (W). A switchgear comprising a shaft (Sw), a connecting shaft (C) provided on the movable body (D), and urging means (Sc, Bk, W1) between the fixed support shaft Sw and the connecting shaft C The form changes with the operation of the opening and closing device, and the range in which the moving body D operates due to the change in the form is a range in which the force acting on the moving body is small (A) and a large range ( “Switching” characterized in that the force is continuously changed from small to large or from large to small with or without slight movement of the moving body. Means "A switchgear characterized by the above-mentioned.
"Switching device 2"
The urging means is a connection shaft (Ib in FIG. 93) and an expansion joint (UV) that changes the distance between the fixed support shaft (Sw) and the connection shaft (Ib). It operates by the vertical movement of the weight falling due to deformation of the elastic body or gravity, and the change in the above form is that a new spring force is added to or removed from one spring force, or a new weight is added to one weight. "Opening and closing device part 1" characterized by adding or removing or moving force vector
"Switching device 3"
The distance (Lbo or Lbc) between the vector of the force (Fb) and the rotation axis (O or C) changes with respect to the rotation body (D) that is rotatably supported around the rotation axis (O in FIG. 6). Then, a large rotational force (Mc) acting around the center of rotation (C), a change in the form in which the force (Fb) changes, or a wheel moving along the sliding surface K (K in FIG. 19). For (Bb), the vector of the force (F) acting in the moving direction of the wheel (Bb) is converted into two component forces (Fd, Fb) having different magnitudes and directions, and the change in the form is provided. "Opening and closing device 1 or 2"
"Opening and closing device 4"
The moving body is a rotating body (D) that is rotatably supported around a rotating shaft (O in FIGS. 61 and 63), and the door stop Gd that prevents rotation of one side of the rotating body D is fixed to the moving body. The connecting shaft (c) and the fixed support shaft (Sw) are connected to each other by C two links (J, A), and the two links (J, A) are connected to the connecting shaft (P ), And the rotation shaft (O), the connection shaft (C), the fixed support shaft (Sw), and the connection shaft (P) are urged to rotate. The crossing angle (Θaj) of the axis lines of the two links (J, A) increases or decreases, approaches a state of being in a straight line or overlapping, and presses the rotating body (D) against the door stop (Gd). Any one of the switchgears 1 to 3 characterized in that
"Opening and closing device 5"
The moving body is a rotating body (D) that is rotatably supported around a rotating shaft (O in FIG. 50), and is a link having the rotating body (D) and the fixed portion (W) as a link. A link device for connecting the rotating body (D) and the fixed portion (W) with a plurality of links (J, A, Jc),
Each of the two adjacent links (D, Jc) constituting the link device is provided with an abutting portion (Gj) that abuts and separates from each other by the rotation of the rotating body, and the two adjacent links Each of (D, Jc) becomes relatively united or separated, and swings between a position (Θ1) and a position (Θ2) where the force acting on the rotating body is small. Any of devices 1 to 3 "
"Opening and closing device 6"
The moving body is a rotating body (D) that is rotatably supported around a rotating shaft (O in FIG. 20), and is a link that uses the rotating body (D) and the fixed portion (W) as a link. A link device that connects the rotating body (D) and the fixed portion (W) with one or more links (J, A,),
A slider (BB) is mounted on one of two adjacent links (A, D) that constitute the link device, and a sliding surface (K) that moves along the slider (BB) is provided on the other. The slider (BB) swings between a position where the force acting on the rotating body is small and a position where the force is large.
"Opening and closing device 7"
The mounting shaft (C) of one of the two adjacent links (A in FIG. 57 (e)) constituting the link device is relatively movable and is attached to the other (D). The transmission of force is temporarily insulated from the "opening / closing device 1-6"
"Opening and closing device 8"
A spring (V in FIG. 60) is attached in place of the link constituting the link "any one of opening / closing devices 1 to 7"
"Opening and closing device 9"
The opening of the rotating body is between “the opening Θd1 of the rotating body when the force changes from small to large” and “the opening Θd2 of the rotating body when the force changes from large to small”. The magnitude of the force acting on the rotating body is less than or equal to the maximum static friction force acting on the rotating shaft, and the angle between adjacent links constituting the switchgear is increased or decreased, or [Any one of opening and closing devices 1 to 8] provided with a releasable restraining means for restraining the rotation of the adjacent links around the connecting shaft at a position where the decrease is increased.
Alternatively, “one of the opening / closing devices 1 to 8” in which a part of the plurality of links (J, A,) between the rotating body (D) and the fixed portion (W) is in contact with the fixed portion.
"Opening and closing device 10"
A link device for connecting the rotating body (D in FIG. 13) and the fixed portion (W) with a plurality of links (J, A, AA), and a connecting shaft (provided on the rotating body (D)) "Opening and closing device 5" characterized in that the other connecting shaft (PP) crosses a line segment (Tcs) connecting C) and the fixed support shaft (Sw) provided in the fixed portion (W).
"Switching device 11"
A link device for connecting the rotating body (D) and the fixed portion (W) by a plurality of links (J, A, AA), and any one of the plurality of links (J, A, AA) Sliding surface K on one side of the fixing part
The wheel B that moves along the sliding surface K is mounted on the other side, and the wheel B and the sliding surface K are in contact with and separated from each other. "
"Opening and closing device 12"
"Any one of opening and closing devices 1 to 11" provided with a damper member for braking the switching operation

A product called a normal door closer has the disadvantage that the door feels heavy when opening the door, and it does not open until it comes out once it enters the building like an entrance door facing the outside of the building like the entrance door It is not attached to doors that are frequently used inside the building, even though it can be attached to doors with few. Even if it is installed, it is often fixed in an open state.
In addition, a normal door closer is equipped with a strong spring and can be attached to a front door that attaches to the strong outer wall of the frame, but it is attached to an indoor door frame that does not have the strength to support the force of the strong spring. It is not possible.
The door closer of the present invention is made to eliminate defects in a product called a normal door closer, and when the door is opened, the door does not feel so heavy that there is no difference between when the door closer is attached and when it is not attached. Not only can it be attached to weak frames such as indoor wooden door frames. In the door closer of the present invention, the door moves with a weak spring, so that the frame of the mounting portion is not broken and the mounting bolt is not pulled out.
As described above, the door closer of the present invention can be used for an entrance door, but is also suitable for an indoor door. The number of doors inside the building is several times the number of doors facing the outside of the building, and the market for goods is large.

However, door closers for indoor doors are not so necessary, and in private spaces, it is not so much because it becomes an obstructive mechanism that has to open the door each time a function that closes automatically passes. Not popular.
Therefore, the present invention is expected to be widely used for entrance doors for the purpose of being superior in terms of performance, price, or aesthetics with respect to all currently used door closers. It is.
In terms of performance, not only does it feel heavy or heavy on the door to be opened, it is excellent in terms of performance deterioration due to wear, there are few failures and long life, and there are few parts and strength is not required for the material It is inexpensive and is excellent in that it can be stored in the device or in a small case because the operating range is an elongated range that does not protrude from the door surface, or a small circle near the pivot of the door.

The drive device for rotating the door of the present invention moves by the force of the spring, and in the range from fully open to just before closing, the door rotates greatly with a small rotation of the drive device, so the drive force is insufficient and the door rotates. Will slow down. Further, in the range from immediately before closing to the closing time, the drive device rotates greatly and the door rotates slightly, so that the drive force is not loaded and the drive device rotates rapidly.
In other words, “deceleration based on the rotational speed ratio between the driving side and the driven side in a normal speed reducer” is reversed. For example, if the drive unit shown in the embodiment of FIG. 13 is moved by an electric motor, the rotation speed of the door can be made constant, and in the range from just before closing to the closing time, it takes time for large rotation of the driving unit. Then the door turns small. In addition, a mechanism that temporarily stops for a long time immediately before closing and prevents rotation against gusts and the like works to prevent a fingernail accident.
A door that moves even with an electric motor does not open at the time of a power outage, but serves as an entrance and leads to a confinement accident. From this point of view, a door that moves with a spring is preferable. However, as described above, the closing device of the present invention has better performance when it is moved by an electric motor than when it is moved by a spring, and the present invention is not limited to a spring but can be applied to a door that is also moved by an electric motor.

The rotating mechanism for rotating the door of the present invention has a feature that a large force acts at the end of the rotation and the force acting before that is small. For example, as in Patent Documents 1 to 3, Patent Document 4 When used in an automatic document feeder that presses down a document of a copying machine as described above, it can contribute to the expansion of the range in which the apparatus can be simplified and adjusted.
The “rotating mechanism in which a large rotational force acts at the end of rotation” is a movement in which the gripping force of the finger joints changes when grasping and lifting the object shown in FIG. It can be used as a technique to move the joints of robots.
It can also be handled as a “rotating mechanism in which a large rotational force acts at the beginning of rotation”, and the shock absorber shown in FIG. 55 resists at the beginning of feeling a shake and follows the subsequent displacement. Like a shock absorber, the restoring force is stored in the spring by the subsequent displacement, and the disadvantage of accelerating against the return swing is eliminated. Thus, the rotation mechanism of the present invention is not limited to doors and can be applied to other industrial fields.

Illustration of a door that rotates slowly and closes securely
Illustration of a door that rotates slowly with one spring Explanatory drawing of the door that rotates strongly at the end Explanatory drawing of the rotation mechanism where a strong rotational force acts at the end of rotation Explanatory drawing of the rotation mechanism of FIG. 3 attached to the door surface Figure of figure 4 Explanatory drawing of a door rotating with a wheel moving on a sliding surface Explanatory drawing of the door of FIG. 6 driven by rotation of a rotating body Figure of figure 7

Explanatory drawing of the door that pauses immediately before closing
Explanatory drawing of the door rotating with one spring that stops just before closing Explanatory drawing of a door that keeps moving even if it stops just before closing Explanatory drawing of the door of FIG. 10 where the rotating shaft of a rotating body moves. Explanatory drawing of the door of FIG. 10 in which the connecting shaft of the rotating body and the link moves Explanatory drawing of the door of FIG. 10 connected to a rotating body with two links

Explanatory drawing of a door with a sealing device attached to a rotating device that moves with a single spring
Figure of figure 15 Operational diagram when the rotating body is in contact with the door and the sliding surface is attached to the door frame Explanation of operation when the rotating body is in contact with the door frame and the sliding surface is attached to the door Operational diagram when the rotating body is in contact with the door and the sliding surface is attached to the door frame Explanation of operation when rotating body is rotated by toggle spring

Operation explanatory diagram of a closing device consisting of a sliding surface close to the pivot of the door and a sliding surface far
Closing device with two cam wheels reciprocating linearly Closing device with cam wheels towing near the pivot of the door Closing device with two cam wheels rotating Figure of figure 21

Operation explanatory diagram of closing device consisting of cam body sliding surface and cam wheel
Operation explanatory diagram of closing device with cam body sliding surface is convex surface Operation explanatory diagram of the closing device whose cam body sliding surface is concave Rotation transmission device having connecting portion for moving wheel in long hole Rotation transmission device having connecting portion of link device Closing device that can adjust closing and sealing operations separately

Operation explanatory diagram of the spring that works only when closed and the spring that works only when sealed
Relay explanatory diagram from spring acting at closing to spring acting at sealing Action diagram of the spring acting only when sealed When a link that attaches a wheel to a rotating body is attached When a link with a sliding surface attached to a rotating body is attached When a spring is attached to a rotating body but a wheel is attached to a link When a spring is attached to a rotating body but a sliding surface is attached to a link

Operation explanatory diagram of the drive unit consisting of cam body sliding surface and cam wheel
Operation explanatory diagram of the drive part where the cam body sliding surface is concave Illustration of drawing method of cam body sliding surface shape Operation explanatory diagram of the drive part where the cam body sliding surface is convex Operation explanatory diagram of drive unit with cam body sliding surface involute

Operation explanatory diagram of connecting part of door consisting of two links
Action diagram of the door rotating in the opening direction Operation explanatory diagram of the connecting part consisting of links bent in an L shape Operation explanatory diagram of the connecting part consisting of links that do not bend into an L shape

Illustration of a door that rotates with a smaller force by reducing the sealing force
Action diagram of latch with low resistance when sealed Explanation of the operation of the latch using a cam on the claw Illustration of latch handle with low resistance when sealed

Explanatory drawing of the door that pauses immediately before closing
Stop device that prevents sealing while decelerating just before closing Stop device that prevents sealing just before closing Sealing device that rotates from fully open and pauses just before closing

Explanatory drawing of a door that reduces impact noise when sealed
A device that seals over time with a vacuum damper A device that seals over time with a pressure damper.

Explanatory drawing of a door that converts dynamic inertia attached to the door into braking force
Sealing device having cam wheels that move simultaneously on two sliding surfaces Sealing device that releases the sealing force when closed

Device that stops doors that suddenly accelerate due to gusts
Explanatory drawing of the inertial force measuring device that expresses the magnitude of the inertial force by expansion and contraction on the spring Explanatory drawing of an inertial force measuring device that expresses the magnitude of the inertial force as a rotation angle

Examples in other industrial fields
Illustration of hand device to grab an egg Explanatory diagram of walking leg device Explanatory drawing of the device that reduces the rotational speed

Other embodiment sealing mechanism explanatory drawing
Illustration of two types of sealing mechanism Operational explanation of sealing device with sliding surface rotating Operation explanatory diagram of wheels moving along two sliding surfaces Sealing device with a lever fulcrum wheel in the middle Sealing device with sliding surface of lever fulcrum in the middle Explanatory drawing of the mechanism where the shaft cores of the two links overlap and seal Explanation of the mechanism in which the shaft cores of the two links overlap and seal with leverage Explanatory drawing of the mechanism in which the shaft cores of the two links are aligned and sealed Explanatory drawing of the sealing mechanism with the axis of the two links in a straight line Explanatory drawing of sealing mechanism provided with switching means of swing link Explanatory drawing of the sealing mechanism where the link cores overlap while decelerating just before closing

Energizing means explanatory diagram
Energizing device that relays two torsion springs Energizing device that relays two springs Energizing device with piston Closing device with leaf spring and slider Closing device with leaf spring and link

Operation explanatory diagram of the sealing device attached movably
Closing device provided with connecting body of rotating body and spring Closing device with string and pulley Operation explanatory diagram of sealing mechanism with sliding surface movably attached

Operation explanatory diagram of the speed reduction mechanism that suppresses the rotation of the link connecting shaft
Operation explanatory diagram of the deceleration mechanism of the four-bar rotation mechanism Operation explanatory diagram of the deceleration mechanism of the 5-bar rotation mechanism Operation explanatory diagram of joint rotation prevention mechanism Operation explanatory diagram of sliding surface that rotates in the direction to open the door

Rotating mechanism explanatory diagram consisting of cam body sliding surface and cam wheel rotating body
Correction of cam body sliding surface Operation explanatory diagram of the involute sliding surface moving device Operational explanation of revolving linear cam body sliding surface Operation explanatory diagram of revolving concave cam body sliding surface

Explanatory drawing of a door with a finger padding prevention device
Operation explanatory diagram of a link device having a link with a bent tip Operation explanatory diagram of a link device having a link with a bent tip

Illustration of the door to open
Operation explanatory diagram of switching means for opening door using check valve Operation explanatory diagram of opening door switching means without using a check valve Operation explanatory diagram of link rotation direction switching means

Explanatory diagram of means for biasing gravity of weight
Operation explanatory diagram of the speed reduction mechanism Canopy operation diagram Operational plan view of sliding door Operational plan view of hinged door Explanatory diagram of door operation powered by potential energy

Explanatory drawing of urging means of leaf spring
Operational explanation of door urged by leaf spring Operation explanatory diagram of laundry basket with small opening force

Explanatory drawing of rotating mechanism that swings the lid up and down
Background art comparison diagram Background art comparison diagram Movement means operation diagram consisting of cam wheel rotating body and cam body Movement means operation diagram consisting of cam wheel rotating body and cam body Movement means operation diagram consisting of cam wheel rotating body and cam body Operational explanation diagram of moving means consisting of involute curved cam body Explanatory drawing of rotating mechanism that swings the lid up and down Explanation of rotation mechanism of wave power generator

Illustration of the entrance door
Explanatory drawing of doors installed indoors and outdoors Explanatory diagram of doors installed indoors Explanatory diagram of doors installed indoors

Explanatory drawing of the means to convert the inertial force attached to the door into braking force
Explanation of operation of means to measure inertial force by changing the gradient of sliding surface Explanation of operation of means to measure inertial force by changing the gradient of sliding surface Explanation of operation of the device that stops at the time of rapid rotation Operation explanatory diagram of means to measure inertial force by expansion and contraction of spring

Explanatory drawing of deceleration means corresponding to change from static friction force to kinetic friction force
Operation plan view of the speed reducer with which the two urging devices interfere with each other Operation plan view of the speed reducer in which two springs interfere with each other

Explanatory drawing of the speed reduction mechanism that prevents the spring from expanding and contracting and receiving inertial force
Operation explanatory diagram of reverse biasing from the circumferential direction to the radial direction of circular motion Operation explanatory diagram of reverse biasing from the circumferential direction to the radial direction of circular motion Operation explanatory diagram of mechanism that releases sealing force at the same time as sealing Operation explanatory diagram of mechanism that releases sealing force at the same time as sealing Explanatory drawing of means to switch wheel movement from circumferential direction to radial direction

The present invention relates to a rotating body that continues to rotate in one direction. The entire rotation range from the beginning to the end of rotation is divided into two ranges so that different magnitudes of force act on each range. Provide technology.
Opening and closing devices that require different operating forces in the first half and second half of the rotation are widely recognized in doors and other industrial fields. For example, when it comes to door rotation, the range of rotation and rotation At the end of this, it is divided into the range where the latch rotates from the time when the latch comes into contact with the door frame W until the door comes into close contact with the door stop. In the former range, weak force acts on the door, A strong force must be applied in the range.
Speaking of industries other than doors, for example, a robot arm that picks up and lifts objects is divided into a range from picking up a piece to a range from picking up to lifting, and the former range is a robot arm. A weak force must be applied to the finger joints, and a strong force must be applied in the latter range.

Many devices that require a large force at the end of rotation are reduced by applying a resistance to the large force acting at the end of rotation, reduced by the gear speed ratio, and reduced by electrical control. There is.
Speaking of doors, door closers with a widely used hydraulic or pneumatic cylinder weaken the "strong spring force that seals the door" by the viscous resistance of oil or air, and rotate the door until just before the door closes. In the final stage of closing the door, the resistance is removed and the door is sealed with great force. Also in Patent Document 13, a force in the direction opposite to the biasing force of the spring is applied to reduce the spring force. The means for rotating the door while resisting such a large force overcomes this resistance and rotates the door. Therefore, when the door is opened, the spring force is increased more than necessary. I make it feel heavy.
In industrial fields other than doors, there are many rotating mechanisms that operate in response to manual or electrical commands by controlling the rotational speed or torque through a reduction gear and a switching device.
The present invention does not rely on electrical control as in the latter, and does not use a means with resistance as in the former, but rather processes mechanically. The distance between the action line and the rotation axis is controlled to change the magnitude of the force. There is a clear boundary between the rotation range of the first half and the second half, and it automatically switches from strong force to weak force or from weak force to strong force. The feature is that the magnitude of the acting force suddenly changes. is there.
The present invention has been made to eliminate the “defects felt heavy when the door is opened” with respect to the door. In addition, “technology to solve this problem” is used in industrial fields other than doors.

The “mechanism of the present invention that applies a small force to the first half of rotation and a strong force to the second half” will be described.
When the door is rotated by applying the same force to the door, the rotational force acting on the door is small when the force is applied to a position close to the door pivot, and the door is acted on when the force is applied far from the door pivot. The rotational force is great.
In a reciprocating slider crank mechanism that converts the rotation of the crank into a linear reciprocating motion of the piston, the force transmitted to the piston decreases as the crank length increases.
The above door is a rotating body that can be rotated and is called a “driven rotating body that rotates around the driven shaft”, and the above-mentioned crank is a rotating body that rotates, and this “rotates around the driving shaft” Speaking of “driving rotating body”, the present invention reduces the “distance between the acting line of the force acting around the driven shaft and the driven shaft” to reduce the “rotating force acting on the door”, This is a rotating mechanism that increases the “rotating force acting on the door”, or the present invention increases the “distance between the action line of the force acting around the drive shaft and the drive shaft” to “act on the door” It is a rotating mechanism that reduces the "rotational force" and increases the "rotational force acting on the door".

In the present invention, by not applying a force in the direction opposite to the rotational direction such as resistance, the force of the spring can be minimized, so that it does not feel heavy when the door is opened.
Even in industrial fields other than doors, the speed reduction device and the switching device are eliminated from the rotating device, thereby simplifying the device and removing the speed reduction resistance due to the speed ratio.

In industrial fields other than doors, it is only necessary to switch the magnitude of the force and finally apply a large force. However, with regard to the door, in the first half of the rotation, the acceleration of the door movement speed accompanying the rotation of the door Is a problem.
The rotation axis of the door (hereinafter referred to as the pivot axis of the door) is vertical, and there is no change in potential energy in the rotation of the door, and a force slightly higher than the “maximum static frictional force acting on the pivot axis of the door” acts on the stationary door. Then, the door starts to rotate, and the door continues to rotate when a force slightly greater than the “kinetic frictional force acting on the door pivot” is applied. If the door pivot does not have rotational resistance, no force is required to rotate the door. If the last large force is applied from the beginning, a large impact sound will be emitted when closing. The door closer is an opening / closing device that rotates the door with a small force to reduce acceleration and finally applies a large force to seal the door.

The pivot axis of the door is vertical, and the minimum force required to start moving a stationary door is constant regardless of the door opening angle.
No matter where you open the door and release your hand, the door will not stay stationary, and at least the minimum rotational force required to start moving is the “maximum rest that works around the door axis. It is necessary to apply a force to the door that is slightly higher than the “frictional force” and that is slightly higher than the “maximum static frictional force acting around the pivot axis of the door” at any position.
Even if the force acting on the door applies the minimum necessary force, as long as the force continues to act on the door, the door accelerates as the door closes, and receives a large impact at the time of closing. In order to reduce the acceleration of the door in order to minimize the impact at the time of closing, it is necessary to avoid applying a force greater than the necessary minimum force, so the force that continues to act on the door is minimized It needs to be kept constant.

The normal door closer reduces the force of the spring acting on the door by resistance, but the present invention reduces the force of the spring without applying resistance and acts on the door. It is necessary to compensate the force and compensate for the reduced amount of the spring force, which exceeds the latter spring force. As a result, the final sealing force was not the same, and the door was sealed with an unnecessarily strong force, resulting in a heavy feeling when opening the door.
In a special environment where a small force is applied, such as “a rotational force that approximates and exceeds the maximum static frictional force,” the rotational resistance around the pivot axis of the door and the air resistance applied to the door contribute to the rotation of the door. The air resistance plays a role in reducing the rotational speed of the door in the same manner as the viscous resistance of oil in a normal door closer. Under the condition where the force acting on the door balances with the air resistance, it approaches a constant speed motion without acceleration.
In order to minimize the acceleration of rotation, the present invention provides a means for keeping the force acting on the door small and allows the door to rotate slowly and tightly sealed at the end of the rotation.

The present invention relates to a “spring-operated door and a rotating mechanism or an opening / closing mechanism serving as a base thereof”, which is made to relieve an impact sound at the time of closing by slowly rotating the door. When opening a door equipped with a large amount of force is required, it was made to eliminate the disadvantage that the door feels heavy.

In order to bring the door into close contact with the door stop, the latch needs to be recessed in the door. There are two types of closing rotation of the door: “Rotating with the work that dents the latch into the door” and “Rotating without accompanying”, which is the rotation without most of the closing rotation, and at the last moment of the closing rotation. Only with "work to dent the latch in the door".
When doing "work to dent the latch in the door", it is necessary to add "force to dent the latch in the door" to the force to rotate the door, and the force required only for the last moment of the closing rotation Is greater than the “force required to rotate the door” in most other rotations.
In the final stage of closing the door, a large force, that is, a sealing force, is required to press the door against the door even though the spring-operated door is weakened and minimized as the door is closed. Many spring-driven doors have the problem of "How to convert the spring force weakened at the last stage of closing the door into a large force to seal the door."

A door closer equipped with a widely used hydraulic or pneumatic cylinder weakens the "strong spring force that seals the door" by the viscous resistance of oil or air, and rotates the door until just before the door closes with the weak spring force. In the final stage of closing the door, the resistance is removed and the door is sealed with great force. In Patent Documents 12 and 13, a force in the direction opposite to the biasing force of the spring is applied to reduce the spring force. In this way, the means for rotating the door by reducing the “power to seal the door at the end” will overcome the resistance and rotate the door, so the door will be rotated by the spring force more than necessary. , "The power to seal the door at the end" is unnecessarily large.
When opening a “closed door with an unnecessarily large sealing force”, a force in the opposite direction, which is the same as the sealing force, is required, resulting in a heavy feeling when opening the door. Also, since the magnitude of the spring force increases as the door is opened, the larger the “sealing force acting on the closed door”, the heavier it feels than necessary as the door is opened. In order to “do not feel heavy when opening the door”, it is necessary to minimize the “spring force acting on the closed door”.

The door closer provided with a hydraulic or air cylinder and Patent Document 13 simply add a function of self-closing, so that the door that rotates with a slight force is bothered to make it difficult to turn.
The self-closing function is not a "necessary function that cannot be avoided", but it is more convenient to keep it open in passages that frequently enter and exit. We have a heavy eye only when going out, but this door closer is a product that you want to remove as soon as you install it in the room. The usual technique is to remove the resistance as much as possible so that the force is transmitted effectively, but a special technique is adopted in a product called a door closer.
Both the door closer and Patent Document 13 reduce the force of the spring by applying a force in the direction opposite to the rotation direction of the door, and transmit the force of the spring to the door inefficiently.

The present invention relates to a driven rotary body whose rotation axis is vertical like a door, and is an opening / closing mechanism in which a force is applied around the vertical driven rotation body rotation axis to rotate the driven rotation body, “Rotating means in the range (A)” that rotates the driven rotating body while keeping the force small, and “Rotating means in the range (I)” that rotates the driven rotating body by increasing the force And an opening / closing mechanism having a “switching means for switching” from the rotating means in the range (A) to the rotating means in the range (I).
For example, by reducing the distance L between the line of action of “force F acting around the driven rotary body rotation axis” and the driven rotary body rotation axis, “rotational force M acting around the driven rotary body rotation axis” "Rotating means in the range (A)" and "Rotating means in the range (I)" that increase the rotational force M by increasing the distance L.

In this way, the present invention does not adjust the force of a large spring by applying a resistance like the above-mentioned viscous resistance or a normal door closer, and the friction resistance or other resistance is opposite to the biasing direction of the spring. Instead of acting in the direction, it adjusts the force of the spring by controlling the "distance between the force line of action and the center of rotation", rather it acts a large force of the small spring, The spring force weakened at the last stage of closing the door is converted into a large force.
Therefore, in order to effectively transmit the force of a small spring to the rotation of the door, the friction is removed as much as possible, and a bearing is actively used for the rotation support shaft. As a result, there is little performance degradation due to wear.
The present invention is characterized in that a weak rotational force acts from the beginning to the end of the closing rotation of the door, and a large rotational force suddenly acts at the end of the closing rotation, and the ratio of the spring force acting on the door is reduced. The door is rotated and the ratio is increased to seal the door. The rotational force acting on the middle and the final rotation are different.

If the “force necessary to dent the latch into the door” acts at the end of the closing rotation, the excessive force is converted into an impact sound. Since the “force required to dent the latch into the door” varies depending on the door, the generation of the impact sound cannot be stopped unless the magnitude of the “large last acting force” is adjusted by the door. In order to stop the generation of the impact sound, it is necessary to unify different latches depending on the door, and there is a difference between the magnitude of the “rotational force acting on the middle rotation” and the magnitude of the “rotational force acting on the final rotation”. It is desirable to make it less.
A normal latch moves in parallel with the door surface, and the “direction in which the force acts on the latch” and the “direction in which the latch moves” are perpendicular to each other. It moves in the same direction as “the direction of the action”, and by making the “force necessary to dent the latch into the door” as small as possible, the “spring force acting on the closed door” is reduced, In addition, the adjustment range is reduced to solve the “problem to reduce the generation of impact noise”. In addition, the force required to open the closed door is reduced by reducing the force required for sealing.

The present invention aims to disseminate in general instead of a normal door closer, and when the door is opened, the door feels light, and it does not stop halfway and closes, and the normal door closer has For example, a normal door closer has a function to stop just before closing even if the door is swept by a strong wind and rotates rapidly. And when it is closed a little, it has a function of fully closing.

A normal door closer has a “characteristic that it is covered with a strong wind and does not rotate rapidly”, and is excellent in that there is no impact when sealed, and the present invention is excellent in that a large force is not required when opening.
A normal door closer can handle a heavy door by increasing the spring force, but the closing device of the present invention prepares the spring force as needed, and increases the spring force. As a result, there is a drawback that it is impossible to cope with a door with a small weight. The advantages of both the conventional door closer and the closing device of the present invention lead to drawbacks.
However, the present invention comprises a link device, and the attachment position of the link connecting point is movable and the structure of the link device changes. In addition to “the door has a function of stopping before closing even if the door is swept by a strong wind and rapidly rotating” and “a function of opening fully when opened a little, and fully closing when closing a little”.

When the door is opened, power is stored in the spring, and the `` door that closes without permission wherever you release your hand '' changes to `` a door that opens fully when it opens a little and opens fully when it closes a little '' To do.
The former `` door that closes by itself '' stores the force in the direction of closing when the door is opened in the spring, while the latter stores `` power to open by itself '' while opening a little, and the `` door that closes by itself '' while it closes a little Store power. The former stores a force for urging in the direction opposite to the rotation direction, and the latter stores a force for urging in the same direction as the rotation direction. The latter adds the “function to open arbitrarily” to the former “function to close arbitrarily”, and the former and the latter share the same members.
As described above, the present invention also has an object to be superior to a normal door closer, and the problem is solved by providing various functions.

As long as the force is applied to the door, the speed of the door will increase, even if it is a door that works with a small force that barely starts moving on a stationary door and does not apply a larger force, that is, it is the minimum necessary. Even when a constant force continues to be applied, it moves at a constant acceleration, and the speed increases with time. As a result, inertial force is attached to the door, and a violent impact sound is generated when the door is closed.
The inertial force is proportional to the square of the speed, and the speed at the time of closing varies greatly depending on the opening of the door when the door is opened and the hand is released, so the inertial force is also greatly different. The inertial force is proportional to the weight of the door and varies depending on the door. Many door closers brake this inertial force to decelerate, but when friction resistance is used as a means, braking is performed according to the magnitude of the inertial force over a wide range of the above-mentioned inertial force. The strong frictional resistance that brakes when the door is wide open and the hand is released will stop the door when the door is released small and the hand is released. In addition, the weak frictional resistance that brakes when the door is opened small and the hand is released will close without opening the door and releasing the hand at all. In addition, the friction resistance means is not so much used because its performance deteriorates due to wear of the friction surface and is affected by temperature.
“Door closer with hydraulic or pneumatic cylinder” brakes by the viscous resistance of oil or air instead of the above frictional resistance, and is excellent in that the performance is maintained for a long time, and the braking force according to the speed Changes, and the doors that are rapidly rotated by the strong wind are braked strongly. Moreover, the state close to the stop state is maintained for a long time just before the closing. However, the hydraulic or pneumatic cylinder is a high-pressure vessel, and there is a problem of oil leakage or air leakage.

Various inexpensive door closers having the same performance as that of “door closers having hydraulic or pneumatic cylinders” have been devised, but Patent Document 1 uses rolling friction of gears, and Patent Document 2 is opposite to closed rotation. The one that reduces the force of the spring that urges in the closing direction using a spring that works in the direction, Patent Document 3 is the one that turns on and off the brake device by operating the centrifugal device against an inertial force exceeding a predetermined magnitude However, each of them reacts to a limited amount of inertial force, and does not cover a wide range like a “door closer equipped with a hydraulic or pneumatic cylinder”.
The impact sound at the time of closing increases even if the rotation speed of the door at the time of closing is not large, and the technique of Patent Documents 1 to 3 stops the door against a slowly rotating door or Will not work at all, and will not work as expected.

Even in Patent Documents 1 to 3, even if “Door Closer with Hydraulic or Pneumatic Cylinder” is used, a “force to reduce the force of the spring urging in the closing direction” is newly applied. It does not change the magnitude of the spring force.
For example, the force of the spring becomes stronger as it is opened, but no means for reducing the force of the spring as it is opened is taken, and the door feels heavier as it opens.
In many cases, when the hand is released from the fully opened position, the inertial force at closing is large even if it rotates with a small force. It has sufficient “force to make close contact with the door (hereinafter referred to as sealing force)”. The inertia force attached to the door is greater than the sealing force. Further, in many cases, the door can be opened more than a full opening, rather than being fully opened, and the sealing force can be increased.
Patent Documents 1 to 3 and “Door Closer with Hydraulic or Pneumatic Cylinder” apply resistance to this, and the door will rotate against this resistance, which is more than a force sufficient to simply rotate the door. If is not stored in the spring, the door will not rotate. This is the only factor that feels heavy when opening the door.

The rotation axis of the door (hereinafter referred to as the door pivot O) is vertical, and there is no change in potential energy in the rotation of the door, so it rotates with a force slightly exceeding the maximum static frictional force acting around the door pivot O. However, it is much smaller than “the force of the spring that rotates the door against the force of braking the inertial force”. In the present invention, the door is simply rotated by “a force slightly exceeding the maximum static frictional force” in the range where the door is rotated, and the acting force is increased in the range where the latch is rotated while being recessed.
The present invention does not rely on power such as electricity as the biasing means, but uses the force of the spring and the vertical movement of the counterweight as the power, and changes the decrease in strain energy and positional energy into the rotational movement of the door. Unlike the door closer that adds a new means to reduce the "power provided by springs, counterweights, etc.", it changes the "power provided to the door" without reducing it, thereby opening the door Sometimes it doesn't feel heavy.

That is, as shown in FIGS. 59 and 60, the closing device of the present invention functions as a lever only when the door is sealed and exerts excessive spring force, or as shown in FIGS. Convert to a large axial force, or add a new force when sealed as shown in FIGS. 67 and 68, or add a counterweight that hangs down only when sealing the door as shown in FIG. Patent Document 4 relates to an electric door that “rotates with a weak force and a strong force acts finally”, and the magnitude of the rotational force and the control of switching thereof are processed electrically. The present invention is not electrically controlled but mechanically switched, and means are different. In addition, the reliability of the apparatus is increased by reducing the number of parts constituting the apparatus. The electric door is not preferable because it has a drawback that the passage is blocked during a power failure.

That is, for example, as shown in FIGS. 6 and 88, the present invention includes a “driven rotating body D that rotates about the driven shaft O” and a fixing portion W to which the driven shaft is attached. And a biasing means (A, B, K) mounted between the driving shaft Sw and the driven rotating body D, and the opening / closing device. The means operates by the strain energy of the elastic body V that bends or expands or contracts in the axial direction, or the potential energy of the counterweight CW that moves up and down, and the rotational force acting around the driven shaft is small. Means "," rotating means in the range of (i) "with the above force, and" rotating means in the range of (a) "to" rotating means in the range of (i) ", or" (i) From "rotating means in the range of" to "rotating means in the range of (a)" above An opening / closing device comprising a “switching means” for switching, wherein the driven rotating body is moved in the same direction by the “rotating means in the range of (A)” and the “rotating means in the range of (ii)”. The "switching means" is continuously applied from a small to a large or from a large to a small with or without rotation of the driven rotating body. “Switching means” for switching, which differs from the lids of Patent Documents 1 to 3 regardless of whether the rotation axis is vertical or horizontal, and belongs to a technical range such as a normal door closer. When the biasing means is operated by the potential energy of the counterweight CW, in the “rotating means in the range (ii)”, the counterweight that moves up and down in the “rotating means in the range (a)”. The opening / closing device is characterized in that the force acting on the driven rotating body D is switched from large to small by adding a counterweight CW2 that moves up and down separately to W1, ”as shown in FIG. In addition, the “switching means” operates largely with a slight rotation of the driven rotating body, so that a separate counterweight CW2 that moves up and down can be added.
“When the urging means operates by the strain energy of the elastic body V, in the“ rotating means in the range of (ii) ”, the elastic body V1 deformed in the“ rotating means in the range of (a) ”. An opening / closing device characterized in that a separate deformable elastic body V2 is added, or a driving rotating body that is energized by the power and rotates about the driving shaft. The driving rotating body is a driving support shaft. An opening / closing device that converts a rotational force acting around the drive shaft into a drive support force acting on the drive support shaft so that the drive support force acts on the driven rotating body. "Distance between the shaft and the action line of the driving support shaft force" is reduced so that the rotational force acting around the driven shaft is small. Around the driven shaft by reducing the "distance between the axis of action of the spindle force" The "rotating means in the range (ii)" having a large working rotational force and the "rotating means in the range (ii)" to the "rotating means in the range (ii)" or the "(ii) range" An opening / closing device comprising a "switching means" for switching from the "rotating means" to the "rotating means in the range (a)",

Furthermore, the provided force is transmitted to the door with an excessively small force, and is an opening / closing device that controls the "distance between the rotating shaft and the action line of the force" to rotate the rotating body, The distance is continuously switched between “the rotating means in the range of (A)” having a small distance, and “the rotating means in the range of (I)” having a large distance, and the distance being changed from small to large or from large to small. An opening / closing device provided with “switching means”, and this technology can be used in industrial fields other than doors including doors.

With such a “rotating means in the range (a)”, the door can be rotated with “a force slightly exceeding the maximum static frictional force”, but the frictional force acting on the pivot axis O of the door that has started to rotate is A force smaller than the maximum static friction force and more than necessary is applied to the door. However, the air resistance acting on the door increases as the speed of movement of the door increases, and when the door rotates with a small force, the force acting on the door balances with the above air resistance, resulting in constant speed motion without acceleration. Get closer. The smaller the force acting on the door, the more the air resistance performs the same function as the oil viscosity resistance of the “door closer with a hydraulic cylinder”.

When the closed door is opened, the same force as the sealing force is applied to the closed door, and the force required to open the door is not reduced unless measures are taken to reduce the sealing force. The present invention provides a latch device that does not require a large sealing force as described in FIGS. 41 to 43, but utilizes an inertial force attached to the door when sealing the door. .
Compared with the force that the latch abuts against the door frame W and pushes the stationary door, the force that pushes and seals the moving door is much smaller. The present invention reduces the force of the spring acting on the closed door by closing the door using the inertial force. It is something to be made.

The closing device of the present invention brakes just before closing when closing from the fully opened state, and keeps rotating with inertia force without braking when closing from a slightly opened position. When the door is opened, the position where “the rotating means in the range (ii)” returns to “the rotating means in the range (a)” is widened so as not to stop even if the hand is released. Such braking does not increase the force of the spring like the resistances of Patent Documents 1 to 3 and “Door Closer with Hydraulic or Air Cylinder”.

Patent Documents 14 to 18 are “a rotating mechanism in which there are two ranges in which forces of different magnitudes act and a clear boundary exists between them” in the rotation range, but differs from the present invention in the following points.

Patent Documents 14 to 16 relate to a lid such as a trunk of an automobile, and Patent Document 17 relates to a document feeding device mounted on an upper surface portion of a copying machine. Both the trunk of the automobile trunk and the document feeder are turned up and down. At the end of the rotation, the trunk lid of the automobile is strongly sealed, and the document feeder strongly presses the document.
Both the lid of the car trunk and the document feeder are horizontal, and the center of gravity moves not only in the vertical direction but also in the horizontal direction as the center of gravity opens. The “rotational moment acting around the rotational axis” changes from moment to moment. To do. In Patent Documents 14 to 17, the spring or the document feeding device is supported by a spring so that the lid or the document feeder is not lowered.
Patent Documents 14 to 17 are the same as the present invention in that a large force acts at the end of rotation, but the spring force is biased in the direction of lifting the lid before the major change, and the biasing direction at the end of rotation. Reverses and urges the lid to push down. Patent Documents 14 to 17 support the lid so that it does not drop, and do not rotate it. In the present invention, the direction of the force acting on the driven rotating body is the same from the beginning to the end of the rotation, and the method is always urged to close the door. Patent Documents 14 to 17 and the present invention are reverse in the biasing direction of the spring.

Patent documents 14 to 17 deal with force balance statically. Time does not matter. On the other hand, in the present invention, the present invention is related to time and deals with motion and motion speed.
For example, the force acting on the door is converted into motion acceleration, and the acceleration is reduced by applying the minimum necessary force.

The rotation mechanism of Patent Documents 14 to 17 and the embodiment of the present invention shown in FIG. 34 have the same structure including a “cam body sliding surface and a cam wheel that moves along the cam body sliding surface”. When moving along the middle part of the surface, a relatively small rotational force is provided, and when the cam wheel reaches the end of the cam body sliding surface, the direction of "force that the cam wheel presses the cam body sliding surface" However, Patent Documents 14 to 17 solve the problem by changing the magnitude of the working force, and the present invention provides a mechanism for providing a large rotational force at the end of rotation. It solves the problem by keeping the magnitude of the working force constant. Therefore, the shape of the intermediate part of the cam body sliding surface is different.

In the present invention, measures are taken to minimize the acceleration of rotation as much as possible. For example, in the case of a door, the minimum force required to start moving a stationary door having a vertical rotation axis is constant regardless of the opening angle of the door.
Even if the force acting on the door is the minimum necessary force, as long as the force continues to act on the door, the door accelerates as the door closes, and receives a large impact at the time of closing. In order to reduce the acceleration of the door in order to minimize the impact at the time of closing, it is necessary to avoid applying a force greater than the necessary minimum force, so the force that continues to act on the door is minimized Kept constant.
No matter where you open the door and release your hand, the door will not stay stationary, and at least the minimum rotational force required to start moving is the “maximum rest that works around the door axis. A force slightly exceeding “frictional force” and slightly exceeding “maximum static frictional force acting around the pivot axis of the door” is applied to the door.

In a special environment where the door rotates with a "rotational force approximating and exceeding the maximum static frictional force," the rotational resistance around the pivot axis of the door and the air resistance applied to the door have a significant effect on the speed of the door. The air resistance plays the role of reducing the rotational speed of the door in the same way as the viscous resistance of the oil of a normal door closer.
Under the conditions where the forces are balanced, the speed is constant, and the rotational resistance around the pivot axis of the door and the air resistance applied to the door approach the state of balancing the force that rotates the door. No closer to constant velocity exercise.

The rotation mechanism shown in FIG. 34 is similar to the rotation mechanism of Patent Documents 14 to 17, but the shape of the intermediate portion of the cam body sliding surface is different. As shown in FIGS. The distance between the line of action of the force that presses the rotating shaft and the rotating shaft is constant, and a constant rotating force is applied around the rotating shaft regardless of the position of the cam wheel at any position in the middle of the sliding surface of the cam body. providing. The rotation mechanism shown in FIG. 34 makes it possible to continue rotating the door with the minimum necessary rotational force, and allows the closing rotation of the door to approach a constant speed motion without acceleration.
That is, the present invention does not merely convert the technique of Patent Documents 14 to 17 when the rotation axis is horizontal but only when the rotation axis is vertical. It solves the “problem of doing” and realizes that a person skilled in the art could not accomplish even after a long period of time, that the door that is moved by a spring “slowly rotates and seals tightly”.

Patent Documents 19 and 20 apply the lever principle as one of the “techniques for applying a large force at the end of the rotation of the door”, but “actually by moving the fulcrum gradually toward the point of action” `` The force that acts on the point gradually increases '' makes it possible to apply a large force at the time of sealing, and it does not keep the force acting on the door constant, it increases as it approaches closing, so it closes just before closing There is a drawback that the door accelerates during the period.
On the other hand, in the present invention, for example, in FIGS. 14 to 19, “the action point discontinuously moves from a position close to the door pivot O to a position far from the door axis O. In FIGS. 13, the crank length of the rotating body of the drive unit is instantaneously reduced immediately before closing to provide a large rotational force to the door.

As described above, the present invention includes “a rotating means in a range where a certain weak force acts” and “a rotating means in a range where a strong force acts”, and there is a clear gap between them. There is a boundary where the "force acting on the door" changes discontinuously or rapidly with little or no door rotation, and the acceleration immediately before closing is reduced. is doing.
The rotation mechanisms of Patent Documents 19 and 20 are provided with “rotating means in a range where a strong force acts” according to the present invention, but “rotating means in a range where a certain force acts” and “ "Switching means" is not provided.

Patent Documents 21 to 23 are sealing devices that operate only at the time of sealing, and are separated from the door when opened and do not participate in the rotation of the door. The swing arm generally includes a swing arm that reciprocates between a stationary state and a closed state, and a return spring that operates to the closed state and returns to the stop state. Is moved from the stationary position to the closed position.
In order to stretch the return spring, a large force is required, and the device does not start in a state where there is no force to seal the door at the end of the rotation of the door as in the present invention.
In the first place, it is a device that seals an accelerated door while decelerating, and is designed to operate when the force to stretch the return spring is sufficient, like an accelerated door. Or it is designed to operate by pushing the door in with a human hand.

Patent Documents 21 to 23 are the same as the present invention in that they include a “sliding surface and a slider that moves along the same”, but the door is sealed under a large force, as in the present invention. Even a small force does not seal the door.
The state at the time of sealing of the devices of Patent Documents 21 to 23 is an unstable state in terms of structural mechanics, and is a state in which a fulcrum supporting the reaction force of the sealing force moves, and only a part of the spring force is used as the sealing force. Not used.
On the other hand, in the present invention, as shown in FIG. 15, the action line of the force that the sealing force acts at the time of sealing approaches the state where the axis of the rotating body is in a straight line, and approaches the state where the link device is stationary. The reaction force of the sealing force is supported.
Only when the node of the structure does not move, the node force works, and the spring force works as a sealing force. When the device can move, the force acts weakly, and when it cannot move, the force acts strongly.

Patent Documents 21 to 23 are also shock absorbers equipped with dampers, and work directly on a door that closes rapidly to decelerate the door just before closing. The shock absorbers of Patent Documents 21 to 23 add resistance close to a collision, and when the door rotation speed just before closing is slow as in the present invention, the door rotation may be stopped and remain stopped. If it does, it will not close again.
On the other hand, the sealing device of the present invention is designed to continue to move even when the door is stopped, and when the rotational speed of the door immediately before closing exceeds a certain speed as illustrated in FIG. It is designed to stop operation and start again when the door stops rotating.
As shown in FIG. 13, the link device that operates in the direction in which the door opens just before closing, and the sliding surface that works in the direction in which the door opens as described in FIGS. The braking force also increases according to the magnitude of the inertial force attached to the door. Again, when the door stops rotating, it starts again.

In the closing device of the present invention, the operation of the device is slow and slow even if the door rotates greatly within the range (A), and if the damper is attached to this, the damper works invalidly. In the range of (ii), the rotation of the door is small and the device operates largely, and the damper works effectively.
When the point of action that remains at the center of rotation moves away from the center of rotation, the door does not rotate, so the spring force does not need to rotate the door, and the point of action moves away from the center of rotation in an unloaded state in an instant. That is, the “switching means” of the present invention is an operation that ends in an instant in an unloaded state.
47 and 48 show an embodiment in which a damper is attached to the closing device of the present invention. The damper works as a “switching means” to slow down the operation of the closing device. Patent Documents 21 to 23 describe a door like a damper. It does not work directly with the door, and does not resist the door closing rotation.
Neither the damper of the present invention nor the device that prevents the rotation of the door will result in an increase in “strength of the spring that rotates the door”. Further, since the damper has a weak spring force for driving the device, a simple damper with low air pressure can function sufficiently.

A door closer with a hydraulic cylinder closes slowly and is an excellent product with low impact noise when closed, but it is expensive due to oil leakage problems. Many inventions including the above-mentioned prior art try to obtain equivalent performance by means of replacing hydraulic cylinders, but as in the present invention, the door until just before closing is `` stopped, There is no “rotating means in the range of (A)” characterized in that it is kept in a “rotating state with a weak force that does not stray”.
For this reason, many inventions address the problem of how to decelerate a door that has been greatly accelerated at the time of closing, and employ braking means and buffering means as means for solving the problem. As in the present invention, “means for controlling the direction in which the force acts” is not taken and the “problem of decelerating the door” is not handled small.

The present invention is such that when passing through a door equipped with a conventional door closer, the door is not opened against the resistance of the door closer, but is allowed to pass through the door portion with low resistance. It is desirable to open and close it freely like an electric door.
The ideal door of the present invention is a “door that does not feel the strength of the spring when it is opened”, and the strength of the spring is as small as possible. The strength of the spring is determined by the force required at the time of sealing. For a door that is closed by a magnetic catch, the force acting on the door does not need to increase at the end of rotation. This rotates with "a force slightly exceeding the maximum static frictional force of the door" and does not require any more force.
However, a door that is closed with a magnetic catch cannot be unlocked without turning the handle, and cannot be locked.
Patent Document 24 relates to a latch structure for preventing breakage, and the latch bolt of the document rotates but also retracts. The resistance at the time of closing is not reduced like the latch device of the present invention. Further, there is no feature of receiving the force that prevents the door from being opened on the side surface of the concave portion that accommodates the latch claw, not the rotation axis of the latch claw.

Patent Documents 25 to 27 relate to “a door in which the spring biasing direction is divided into an opening direction and a closing direction with a certain opening angle of the door as a boundary”. It does not deal with “a door that opens freely until it is fully opened and then closes a door that is fully closed when it is fully closed. In addition, the “opening angle of the door that is divided into the direction in which the spring biasing direction is opened and the direction in which the spring is biased” in Patent Documents 25 to 27 differs between when the door is opened and when the door is closed.
Since the force to rotate the door is small, it is not necessary to store as much force as the left to store the “power to open it freely until it is fully opened” with a slight rotation when the door is opened slightly. The same applies when closing the door a little.

The opening / closing device described below includes a door frame W (fixed portion), a door D (driven rotating body) that rotates about a pivot O (driven body rotating shaft) of the door provided on the door frame W, and a door. The connecting shaft C provided on D and the fixed support shaft Sw provided on the door frame W (fixed portion) are connected by urging means, and both ends of the urging means are the connecting shaft C and the fixed support shaft. It is composed of Sw and is attached to the door D via the connecting shaft C and is attached to the door frame W (fixed portion) via the fixed support shaft Sw.
One of the connection shaft C and the fixed support shaft Sw, which are the support shafts at both ends of the urging means, is provided at a position close to the door pivot O (driven body rotation shaft) and the other at a position farther away. A support shaft provided at a position close to the (driven body rotation shaft) is referred to as a near mounting shaft Sn, and a support shaft provided at a far position is referred to as a far mounting shaft Sf.
Further, hereinafter, the rotating body that provides the rotational force is referred to as a driving rotating body, and the rotating shaft thereof is referred to as a driving rotating body rotating shaft. This is called the drive rotor rotation axis. Similarly, a member that provides force is called a driving body, and a member that provides force is called a driven body.

The biasing means will be described.
The biasing means of the switchgear that is moved by a spring is an expansion / contraction joint in which the distance between the support shafts at both ends changes. When the expansion / contraction joint is a single body, the tension spring V and the push spring U are used in the axial direction. An elastic body that expands and contracts, an elastic body that undergoes bending deformation such as a leaf spring VW shown in FIG. 70, or an elastic body that undergoes bending deformation and curves like a leaf spring VW shown in FIG. It is a means for applying a nodal force to the support shafts at both ends.

When the expansion / contraction joint is a composite, for example, as shown in FIGS. 68 and 69, a predetermined amount as shown in FIGS. 59 and 60, such as a piston rod A reciprocating by a push spring U charged inside the cylinder Jh. A complex including an action body A that moves in the axial direction like an action body A that reciprocates along a passage K by a pulling spring V, for example, 2 connected by an intermediate connection shaft P as shown in FIGS. There are composites composed of two rigid links A and a rotating body J, in which the two rigid bodies are bent and the distance between the support shafts Sw and C at both ends is changed by the torsion spring UV.

In addition, for example, as shown in FIG. 7, a connecting shaft P is provided at the tip of a rotating body J that is rotationally biased by a pulling spring V to connect the link A, and the rotation of the rotating body J is linearly reciprocated by the link A. A composite body in which a wheel B is mounted by providing a wheel rotation shaft Ib at the tip of a rotating body link A rotated and biased by a tension spring V as shown in FIG. For example, FIGS. 10, 13, 1, and 63 change the radius of rotation, including those that function as levers, all of which are “the distance Lf between the force action line F and the center of rotation”. Is a means for changing the magnitude of the force acting on the door D (driven rotor). The rotational force acting around the center of rotation is converted into an infinite pressing force so that the force action line F passes near the center of rotation.

These opening / closing devices have two links: a door frame W (fixed portion) and a door D (driven rotary body) that rotates about a pivot O (driven body rotary shaft) of the door provided on the door frame W. A link device configured as a member, wherein the urging means for connecting the connecting shaft C provided on the door D and the fixed support shaft Sw provided on the door frame W (fixed portion) is one or more link devices. Forming.

“Rotating means in the range of (A)” and “Rotating means in the range of (ii)” having a small rotational force acting on the door D (driven rotating body) and a force acting on the door D (driven rotating body) An opening and closing device comprising a "switching means" for switching from small to large or from large to small,
"Rotating means in the range of (A)" and "Rotating means in the range of (I)" are defined between the line of action of the force acting around the door pivot axis O (driven body rotating shaft) and the center of rotation. As the distance changes, the rotational force acting around the door pivot O (driven body rotational axis) changes or the magnitude of the force acting around the door pivot O (driven body rotational axis) changes. A means for setting the force acting on the (driven rotating body) to two different magnitudes, and “switching means” is a releasable restraining means for restraining the distance between the line of action of the force and the center of rotation. An opening / closing device comprising:
Speaking of an opening / closing device in which the rotational force acting around the pivot axis O (driven body rotating shaft) changes, as means for making the forces acting on the door D (driven rotating body) two different magnitudes, FIG. In the eighth embodiment, one of the connection shaft C and the fixed support shaft Sw, which are the support shafts at both ends of the urging means, is provided at a position close to the door pivot O (driven member rotation shaft), and the other is provided at a position far from it. The support shaft provided at a position close to the door pivot axis O (driven body rotation axis) is movably attached along a path continuing from a position near the door pivot axis O (driven body rotation axis). A support shaft provided at a position close to the door pivot O (driven body rotating shaft) is constrained to a position near the door pivot O (driven body rotating shaft), and the restraint is released to move to a far position. An opening / closing device comprising a restraining means.
Even if the support shaft provided at a position far from the pivot axis O (driven body rotation shaft) of the door is moved, the change in the distance between the force action line and the center of rotation is small, and the support shaft provided at a close position is required. Move.
However, if the movement of the support shaft provided at a position close to the pivot axis O (driven body rotation axis) of the door is limited to a passage continuing from a close position to a position far from the close position, the distance between the force action line and the center of rotation is There is a limit to the size, and there are means for discontinuously moving the line of action of the force so as to have two different sizes as shown in FIGS. FIG. 13 shows one of means for making two different magnitudes by changing the magnitude of the force acting around the pivot axis O (driven body rotation axis) of the door.

The structure and function of FIG. 1 will be described.
FIG. 1 is an operation explanation plane for explaining the case where the biasing means for connecting the connecting shaft C provided on the door D and the fixed support shaft Sw provided on the door frame W (fixed portion) is an elastic body extending and contracting in the axial direction. In the figure, one end of a spring V is attached to a connecting shaft C provided on a “driven rotary body D rotating around a driven rotary body rotation axis O”, and the other end is attached to “driven rotation An opening / closing device with a structure that is attached to the fixed support shaft Sw provided on the fixed portion for mounting the body rotation shaft, and one of the support shafts at both ends of the spring is mounted in the vicinity of the driven rotation body rotation shaft. It is a "device that rotates the door" with a structure that simply connects the two with a spring.
The “fixed portion for attaching the driven rotating body rotating shaft” is the door frame W or a wall surface in the vicinity thereof. Hereinafter, the “door frame W or a wall surface in the vicinity thereof” is collectively referred to as “door frame W”.
In FIG. 1, the tension spring V is illustrated as an axial core line in FIGS.
The door D moves circularly around the pivot axis O of the door, the door immediately before closing is indicated by D10 as a solid line, and the door when fully opened is indicated by D100 and indicated by a dotted line. The numerical values attached to the end of the signs of the door D and the pulling spring V indicate the opening angle of the door D with 0 when the door is closed.
The position of D10 indicated by a solid line is considered to be a position where the latch hits the door frame W at a position where the closed door D is slightly opened, and the latch starts to be recessed inside the door. The position is a position where a strong rotational force begins to act, and the opening angle of the door D when the strong rotational force begins to act is not specified.

In the structure in which one of the support shafts at both ends of the tension spring V is close to the pivot axis O of the door and the other is remote, the fixed support shaft Sw is close to the pivot axis O of the door and the connecting shaft C is far away as shown in FIG. However, FIG. 1 illustrates a case where the connecting shaft C is close to the door pivot O and the fixed support shaft Sw is far away. In either case, by “making one fulcrum of the spring close to the door pivot O”, the axis of the tension spring V, that is, the line of action of the force acting on the door, passes through a position close to the door pivot O, Even when the spring force is set to be large to tightly seal the door, the "force that rotates the door" is changed to "a force that barely starts to move the stationary door", that is, a "small force that exceeds the maximum static friction force μmax" I can do it.
The magnitude of the moment of force acting on the door is represented by the product FL of the magnitude F of the spring force and the “distance L between the action line of the spring force and the door pivot O”. Even if the magnitude F of the spring force is large, if one fulcrum of the spring is brought close to the pivot axis O of the door, the rotational force acting on the door is reduced. That is, even when the spring force is large, the force when opening the door is reduced by “making one fulcrum of the spring close to the pivot axis O of the door”, and the door does not feel heavy.

When one end of the spring connecting the driven rotor and the fixed part is attached in the vicinity of the driven rotary body rotation axis, the "action line of spring force and the pivot axis O of the door and The distance L ”can be kept small, the spring length does not change, the force acting on the rotating body is small even when the spring force is large, and the acceleration of the rotational speed is small.
3 and 4 to be described later, when one end of the spring is attached in the vicinity of the rotation axis of the link A as recognized by the rotation when the link A is sealed, the rotational speed of the link A is slow and accelerated. Few.
When there is no change in the length of the spring, the door does not rotate, the length of the spring changes, the magnitude of the spring force changes, the strain energy of the spring decreases, and the door moves. The strain energy of the spring is converted into the kinetic energy of the door and the hand movement speed is accelerated, but the acceleration of the door is related to the change in the magnitude of the spring force, and not to the magnitude of the spring force.
For example, as shown in FIG. 1 (a), when the positions of the connection shaft C and the fixed support shaft Sw where the fulcrums at both ends of the spring are attached are determined between the connection shaft C and the fixed support shaft Sw by the opening degree of the door D. The distance of the door is determined, the rotation angle of the door and the change in the distance are determined, the amount of spring expansion and contraction is determined by the door rotation angle regardless of the spring strength, and the amount of change in the spring strength regardless of the spring strength Is decided. Therefore, even when the spring force is set to be large when the door is sealed by tightening with the turnbuckle to close the door, the change in the spring length is the same and the closing speed is not accelerated.

Since the maximum static friction force μmax is greater than the kinetic friction force, if a `` small force slightly exceeding the maximum static friction force μmax '' continues to act on the door that has started moving with `` a small force slightly exceeding the maximum static friction force μmax '', Although it continues to rotate with greater force than necessary and accelerates, air resistance acts on the door that has started rotating.
In the range where the force acting on the moving door is small, the "force acting on the door" approaches the balance between the rotational resistance around the pivot axis O of the door and the air resistance acting on the door, and the door moves at a constant speed without acceleration. It approaches the state to do. Since the door remains stationary unless it is “a force equal to or greater than the maximum static frictional force μmax”, “a force slightly exceeding the maximum static frictional force μmax” is the most desirable in order to approach the constant speed motion state.
The switchgear in FIG. 1 keeps the minimum necessary force to keep acceleration as low as possible.

Each of FIGS. 1A to 1D will be described.
The rotating device of FIG. 1 works to reduce the rotation of the door even if the spring force is maximized by reducing the “distance L between the line of action of the spring force and the pivot axis O of the door”. It is intended to prevent you from feeling heavy even if you open the door at the same time.
Comparing Fig. 1 (a) and Fig. 1 (e), as the door is opened, the spring is stretched to increase the spring force. Unlike Fig. 1 (e), the spring force is increased. Even if it becomes large, the force that acts on the rotation of the door becomes small, and even if the door is opened, it does not feel heavy.
For doors that are subjected to different forces at the end of rotation, the degree of feeling heavy when the doors are opened differs depending on whether the closed doors are opened or not. A strong force is acting on the closed door, and a weak force is acting on the door after it is opened slightly.
When opening a closed door, the door will not open unless a force of the same magnitude as the sealing force is applied in the opposite direction. Even doors that are sealed by applying the force of a weak spring strongly require a strong force when opening a door that is closed with a strong force and feel heavy. When the closed door is opened and further opened, the spring force increases as the door is opened, but the door suddenly feels light when entering the area where the sealing force does not work.

In the process of closing the opened door, the spring contracts and the spring force decreases as the door closes.
Comparing Fig. 1 (a) and Fig. 1 (d), in the case of Fig. 1 (d), the "distance L between the line of action of the spring force and the pivot O of the door" increases even if the spring force becomes small. The force that acts on the rotation of the door increases. The force that acts at the end of the rotation will be sufficient to seal, if at most. However, the closing speed of the door accelerates rapidly as it closes.
In the case of FIG. 1 (a), the force acting on the rotation of the door is small, so the closing speed does not increase so much. However, unlike the case of FIG.
As long as one end of the spring is close to the pivot axis O of the door regardless of FIGS. 1A and 1D, it does not feel heavy even if the door is opened as the door is opened. However, the magnitude of the force acting at the acceleration of the closing speed and at the end of the rotation is much larger than that in FIG.
When a torsion spring is loaded around the rotation axis of the driven rotating body and rotates, the door feels heavier as the door is opened, as shown in FIG. 1 (a), and rotates as the door is closed. Although the force is lost, when the periphery of the rotating shaft of the driven rotating body is pulled by a pulling spring as shown in FIG. 1, the door does not feel heavier as the door is opened, as in FIG. As the door closes, the rotational force increases.

FIG. 1 (b) shows the position of the connecting axis C shown in FIG. 1 (a) close to the door pivot O, and FIG. 1 (c) shows the position away from the door surface. ) Is obtained by bringing the position of the connecting shaft C shown in FIG. 1C close to the pivot axis O of the door.
In the case of FIGS. 1A and 1B, the “distance L between the line of action of the spring force and the door pivot O” increases as the door is opened. The case of FIG. 1A is a case where the change is large, and the case of FIG. 1B is a case where the change is small. As the door is opened, the rotational force acting on the door increases. In order to open the door, a large force is required as it opens. Also, the rotational force acting on the door when it starts to close from when the door is fully open is large and decreases as it closes.
In the case of FIGS. 1C and 1D, the “distance L between the line of action of the spring force and the door pivot O” does not increase as the door is opened. Even if the spring strength increases when the door is opened, the rotational force acting on the door does not increase. Also, the rotational force acting on the door when it starts to close from when the door is fully open is large and decreases as it closes.

In the case of FIGS. 1B and 1D, the “distance between the connecting axis C and the door pivot O” is smaller than in the cases (a) and (c). The size of the “circular movement” is small, and the change in the spring length is small. The magnitude of the spring force changes due to the change in the length of the spring, and the strain energy of the spring changes due to the change in the magnitude of the spring force. Since the change in the strain energy of the spring becomes the change in the kinetic energy of the door, the smaller the change in the magnitude of the spring force, the less the acceleration. In order to reduce the acceleration of the door, it is necessary to reduce the change in the magnitude of the spring force as much as possible. Use a spring with low rigidity and a long natural length, and change the spring length as little as possible. That is, “to bring one fulcrum of the spring close to the pivot axis O of the door”.

1A to 1D, the fixed support shaft Sw is a point to which a force for pulling the door is applied, and is referred to as a pulling point. The connection axis C is a point that receives a force for pulling the door, and is referred to as a point to be pulled.
Hereinafter, the support shaft on which the force acts on the driven rotating body will be referred to as a towed support shaft, and the member connected to the towed support shaft will be referred to as an action body. The shaft is called the traction shaft.

The door opening and closing device of the present invention has a “range from fully open to just before closing (A)”, and the acceleration of the closing speed is small as shown in FIG. 1), as shown in Fig. 1 (d), the force that acts at the end of the rotation is large. In order to minimize the acceleration of the closing speed, the large force that acts at the end of the rotation is minimized. This means is limited to the last moment. In FIG. 1, the means moves the end of the spring near the door pivot O to the last moment of rotation. The distance L "is suddenly increased, or the end of the spring far from the door pivot O in FIG. 1 is moved at the last moment of rotation to activate the sealing device far from the door pivot O. Suddenly, the distance L between the line of action of the spring force and the pivot axis O of the door It is intended to hear.

The door opening and closing device according to the present invention is from a “door rotating device” that works weakly in the “range from fully open to just before closing (A)”, and from “just before closing to when closing”. It is an opening / closing device relayed without stopping by the “device for sealing the door” that works strongly in the range (I), and the “device for rotating the door” of the door opening / closing device of the present invention is shown in FIG. As in (d), the mounting shaft Sn close to the biasing means is mounted near the driven rotating body rotation shaft.
1 (a) to 1 (d) show a rotating device provided with "rotating means in the range (A)", which can rotate the door until it comes into contact with the door stop. "Does not have the power to seal the door and does not have" rotating means in the range of (I) ".
The rotating device of FIGS. 1A to 1D does not have “the force μ that dents the latch inside the door” at the position of the door D10 immediately before closing, and does not stop at the “device that seals the door” separately prepared. When relayed, the “force to dent the latch inside the door μ” is generated separately.
When the towing point, the towed point and the center of rotation O of the door are in a straight line and the "extension line of the spring axis" passes through the door axis O, the rotation of the door stops. In the case of FIGS. 1 (a) and 1 (b), the state immediately before the closing is close to the stopped state and the vehicle is decelerated. In FIGS. 1 (c) and 1 (d), the spring axis is far from the pivot axis O of the door. In a certain state, it has the power to start the “device that seals the door”.
1 (a) to 1 (d), even when there is no force to rotate the door at the position of the door D10 immediately before closing, the closing device continues to rotate and relays to the “device that seals the door” without stopping. It is what is done.

A means for increasing the force at the end of rotation will be described.
The rotating device in FIGS. 1A to 1D must be relayed without stopping at a separately prepared “device for sealing the door”.
In the door drive device of the present invention in which the rotational force acting on the door becomes strong at the “last stage of the closing rotation”, the “distance L between the line of action of the spring force and the door pivot O” is suddenly increased. And suddenly, there is something that makes the “distance between the point of action of the force and the fulcrum of the lever” smaller,
In the former, the direction of the force acting on the door suddenly starts to move as shown in FIGS. 2 to 8, and the point of action of the force acting on the door as shown in FIGS. There are those that suddenly move away from each other, and those that suddenly start to move in the direction of the force that the cam wheel presses the sliding surface of the cam body as shown in FIGS. As shown in .about.40, there are those in which the rotating body composed of two links becomes one.
Any of these means solves the “problem of the present invention that tightly seals at the“ last stage of closed rotation ”despite rotating with a weak force”.

The door drive device of the present invention in which the rotational force acting on the door becomes stronger at the “last stage of closing rotation” is relayed from “the device that rotates the door” to “the device that seals the door” and consists of two devices. And “the operation of rotating the door” and “the operation of sealing the door” can be broadly classified into those composed of a single device.
In general, the rotation of the drive device that gives rotation to the door is small in the “process of rotating the door” and large in the “process of sealing the door”. When the rotation of the driving device is small in the “process of rotating the door”, it becomes means for rotating the door greatly with a little energy, and when the rotational force of the driving device is insufficient, it becomes means for slowly rotating the door.
Also, because the rotation of the driving device is large in the “sealing process of the door”, that is, the position of the door when the device for sealing the door is started, or the rotational force acting on the door suddenly occurs in the “last stage of closing rotation” As you get stronger, the door position can be wider. The position that distinguishes “range from fully open to just before closing (A)” and “range from just before closing to when closing (Yes)” is not a boundary but an area. This is because it is difficult to design such that the device for sealing the door is started at the moment of passing through the limited door position or that the rotational force acting on the door suddenly increases.
In the present application, a region where the device for sealing the door starts or the rotational force acting on the door suddenly increases in the “last stage of closing rotation” is referred to as “immediately before closing”.

In FIG. 1, a connecting shaft C provided on a driven rotating body and a fixed support shaft Sw provided on a fixed portion are connected by a tension spring V to rotate the driven rotating body around the driven rotating shaft. The shaft C is positioned close to the driven rotary shaft and the fixed support shaft Sw is positioned far from the driven rotary shaft. FIGS. 2 to 5 are fixed to the door as in the embodiment of FIG. The connecting shaft C positioned close to the driven rotary shaft is movably attached to the door so that the fulcrum of the spring moves away from the position close to the driven rotary shaft. It is a thing.
FIGS. 2 to 5 show that the “distance L between the line of action of the spring force and the pivot axis O of the door” is small by moving the connecting shaft C located close to the driven rotary shaft of FIG. (1) Rotating means in the range "and" Rotating means in the range (ii) "having a large" distance L between the action line of the spring force and the door pivot O ". A single spring is used to process “the operation of rotating the door” and “the operation of sealing the door”.

2 to 4 show that the connecting shaft C provided on the door D and the “fixed fulcrum Sw fixed to the door frame W” are connected by a continuous body AV in which a pulling spring V and a link A are connected in series. The connecting shaft C is pulled by the force of the spring V, and the door D is closed and rotated around the pivot axis O of the door in the direction indicated by the arrow A in the figure.
2 and 4, the link side end of the continuum AV is attached to the connecting shaft C provided on the door D, and in the case of FIG. 3, it is attached to the fixed support shaft Sw. 2 and 4, the end on the spring side of the continuum AV is attached to the fixed support shaft Sw, and in the case of FIG.

2 to 4 show that the position of the moving support shaft Sj in the intermediate connecting shaft of the continuum AV is kept in the region in the vicinity of the pivot axis O of the door in the “rotation range before starting the sealing operation (A)”. The distance L between the line of action of the force and the center of rotation is reduced, and the door is rotated by the reduced moment M of force. In this embodiment, the distance L between the line of action of the force and the center of rotation is increased by moving the area outside the vicinity, and the door is brought into close contact with the door stop by the increased moment M of the force. Here, the axial center line of the tension spring V is a force action line, and the direction of the force action line changes as the position of the moving support shaft Sj changes.

2 to 4 have a restraining means for keeping the position of the moving support shaft Sj in a region near the door pivot O, and by moving the restraint, it is moved out of the region near the door pivot O.
In the case of FIG. 2, the wheel B mounted on the moving support shaft Sj moves along the sliding surface K1 of the boundary wall K so that the position of the moving support shaft Sj is kept in the region near the door pivot O. As the wheel B moves away from the wall K, the "distance L between the spring force action line and the door pivot O" is suddenly increased. The same applies to the embodiments of FIGS.
Hereinafter, the wheel is a slider that moves along a predetermined path, and means a moving body that has little friction during movement.
In the case of FIGS. 3 and 4, while the link A hits G1 or Gd, the position of the moving support shaft Sj is kept in the region near the door pivot O, and the link A moves away from G1 or Gd. Suddenly, the "distance L between the line of action of the spring force and the door pivot O" is increased. The same applies to the embodiment of FIG.

D100 indicated by a solid line in FIG. 2 (a) indicates a fully open state, and D0 indicated by a solid line in FIG. 2 (b) indicates a closed state. FIG. 2A shows a series of operations from the fully open state to the closed state, and FIG. 2B shows a series of operations from the closed state to the fully opened state. The door rotates in the direction of the arrow in the figure, and links A, pulling springs V, connecting shafts C, wheels B, and wheel rotating shafts Ib shown at a plurality of locations indicate positions moved with the rotation of the doors, The subscripts A, V, C, B, and Ib correspond to the subscripts of the door D and correspond to the respective rotation angles of the door D.

In FIG. 2, the continuous body AV in which the spring V and the link A are connected in series always tries to keep a straight line, and when the wheel B does not contact the sliding surface K1 of the field wall K, the straight line is kept. When moving along the sliding surface K1, it bends about the position of the moving support shaft Sj.
When the door rotates in the closing direction as shown in FIG. 2A, the wheel B moves along the sliding surface K1 of the boundary wall K, but rotates in the direction in which the door opens as shown in FIG. When the wheel B moves along the sliding surface K2 of the boundary wall K, the continuum AV becomes a straight line. When the door rotates again in the closing direction, the wheel B moves along the sliding surface K1 of the boundary wall K.

The embodiment of FIG. 4 is also a spring mechanism that applies a large force at the final stage of the closing rotation, and depends on whether or not the link A hits G1 or Gd. The distance L ”with respect to the pivot axis O is increased, and the embodiment of FIG. 28 is the same.
In the case of FIG. 28 and FIG. 2, as the door D is closed and rotated, the bent continuous body AV tends to be in a straight line. In the case of FIGS. 3 and 4, the bent continuous body AV is further bent.
In the case of FIGS. 3 and 4, when the tension spring V rotates around the connecting shaft Sj and the tension spring V and the contact G1 or Gd are on the same side with the axial center line of the link A as a boundary, the link A and the contact G1 Or it contacts Gd, and when it is on the opposite side, link A hits and leaves G1 or Gd. The position where the link A hits and separates from G1 or Gd is when the axial core line of the tension spring V or its extension line crosses the rotation axis Sw or C of the link A.

3 and 4, D100 shown in FIG. 3A shows a fully open state, D11 shown in FIG. 4B shows a state when the rotation before the start of the sealing operation is completed, and FIGS. Through the rotation before the sealing operation shown in the figure starts, the link A continues to contact G1 in FIG. 3 and Gd in FIG. (C) D9 shown in the figure shows a state in which the latch hits the door frame W at a position where the closed door D is slightly opened and the latch is recessed into the door, and the sealing operation is started. However, it rotates around the fixed support shaft Sw in FIG. 3 and around the connection shaft C in FIG. (D) D0 shown in the figure indicates a closed state.

The operation of the embodiment of FIG. 3 will be described.
In FIG. 3, the link A is rotatably supported around the fixed support shaft Sw, and the position of the fixed support shaft Sw is bounded by the spring shaft core line Zv in the “rotation range (a) before the sealing operation starts”. In the region (good) not including the pivot axis O of the door, the force of the tension spring V acts to rotate the link A around the fixed support shaft Sw in the direction of arrow A in the figure. The rotation in the direction is stopped when the link A hits and comes into contact with G1, and the position of the movement support shaft Sj is kept in the region near the pivot axis O of the door by the intermediate connection shaft of the continuous body AV. As a result, the distance Lv between the axial center line Zv of the tension spring V, that is, the force acting line Fv, and the door pivot O is reduced, and the door is rotated by the reduced moment M of force.

When the position of the fixed support shaft Sw is within the region (ah) including the door pivot axis O with the spring shaft core line Zv as a boundary in the “rotation range after starting the sealing operation (i)”, the tension spring V The force acts to rotate the link A around the fixed support shaft Sw in the direction opposite to the direction of the arrow A in the figure, and the rotation in the direction opposite to the direction of the arrow A in the figure is stopped by the contact of the link A with G2. It is done. As a result, the position of the moving support shaft Sj is moved out of the region near the door pivot axis O, the direction in which the spring axis Zv is directed is changed, and the distance L between the force action line and the center of rotation is increased. Then, the door is brought into close contact with the door by the moment M of the increased force.
4, as in FIG. 3, when the sealing operation starts, the link A rotates to move the moving support shaft Sj, the direction in which the spring axis Zv is directed changes, and the door is opened by the increased moment M of force. This is an example in which the contact is made in close contact.

A method of adjusting the force for rotating the door in the range (A) and the force for sealing the door in the range (I) will be described.
One fulcrum of the tension spring V is attached to the moving support shaft Sj provided at the tip of the “link A that rotates freely around the connection shaft C provided on the door”, and the other fulcrum is fixed to the door frame W. Attach to the fixed support shaft Sw. The door D is closed and rotated in the direction of the arrow a in the figure around the pivot axis O of the door.
In FIG. 4, N1 is a screw attached to the link A, Gj1 is an adjustment bolt inserted into the screw N1, and the distance lg1 from the screw N1 to the tip of the adjustment bolt Gj1 can be adjusted by turning the adjustment bolt Gj1. . Similarly, each of N2, Nd, and Nw is a screw that attaches to the door D, link A, and door frame W, and Gj2, Gjd, and Gjw are adjustment bolts that are inserted into the screws N2, Nd, and Nw, respectively, and adjustment bolts Gj2, By turning Gjd and Gjw, the distances lg2, lgd and lgw from each screw to the tip of the adjusting bolt can be adjusted.

In FIG. 4, a link A that is rotatably supported around a link support shaft C, a driven rotary body D that is rotatably supported around a driven shaft O, and the driven shaft O are fixed. A fixed portion W, a moving support shaft Sj is provided at the end of the link A opposite to the link support shaft C, a spring V is connected to the moving support shaft Sj, and the moving support shaft of the spring V is connected. A spring support shaft Sw is provided at the end opposite to the shaft Sj, and one of the link support shaft C and the spring support shaft Sw is attached to the fixed portion W, and the other is attached to the driven rotating body D. An opening / closing device having a structure and a releasable restraining means Gd that restrains the rotation of the link around the link support shaft C and restrains the movement of the movable support shaft.
The releasable restraining means Gd is placed on the link A so as to prevent the link A from rotating in one direction around the link support shaft C (i), and to move the movable support shaft Sj to the driven shaft O. At or near the position of the drive shaft, allowing it to separate and rotate in the other direction so that the movable support shaft Sj is separated from the vicinity of the driven shaft O, and the driven rotating body D An opening / closing device that causes the moving support shaft Sj to move away from the vicinity of the driven shaft O when the spring V crosses the position of the link support shaft C at the predetermined opening degree.
Other embodiments of the structure of FIG. 4 are shown in FIGS.

29 to 33, the releasable restraining means includes a wheel and a sliding surface that moves along the wheel, and the wheel and the sliding surface are in the vicinity of the driven shaft, When the link is attached to the driven rotating body, one is attached to the link and the other is attached to the fixed part, and when the link is attached to the fixed part, one is attached to the link and the other is attached to the driven rotating body. Then, one of the driven rotating bodies revolves around the driven shaft while moving along the other by the rotation of the driven rotating body, and the driving support shaft is driven while the wheel is in contact with the sliding surface. At the position of the shaft or in the vicinity of the driven shaft, the wheel is separated from the sliding surface at a predetermined opening degree of the driven rotating body, and the driving support shaft is separated from the vicinity of the driven shaft. Opening and closing device.

The opening of the rotating body is between “the opening Θd1 of the rotating body when the force changes from small to large” and “the opening Θd2 of the rotating body when the force changes from large to small”. The magnitude of the force acting on the rotating body is less than or equal to the maximum static friction force acting on the rotating shaft, and the angle between adjacent links constituting the switchgear is increased or decreased, or The switchgear according to any one of claims 1 to 8, further comprising a releasable restraining means for restraining the rotation of the adjacent links around the connecting shaft at a position where the decrease is increased.
Alternatively, an opening / closing device in which a part of the plurality of links (J, A,) between the rotating body (D) and the fixed portion (W) is in contact with the fixed portion.
In most of the embodiments, when the door is opened, the opening angle of the driven rotating body when switching from “rotating means in the range (A)” to “rotating means in the range (I)” and the door are closed. The opening angle of the driven rotating body when the driven rotating body reversely rotates and switches from the “rotating means in the range (ii)” to the “rotating means in the range (a)” is different. Characteristic switchgear "
The “switching means” at the time of closing involves a slight rotation of the door, and the “switching means” at the time of opening has a large resistance unless accompanied by a large rotation of the door.
The sealing sliding surface with slight rotation of the door is different from the restoring sliding surface where the door rotates greatly.
When it is in the range between the opening Θd2 of the rotating body, even if there is no force to rotate the door due to the spring force, it can be rotated only by the inertia force of the door, it can be sealed no matter where you release your hand It reaches.
In FIG. 46, when the sliding surface comes into contact with the door frame, a part of the rotational force transmitted to the door is not effective as a force for rotating the door. The same applies when the link in FIG. 72 contacts the door frame.

The operation of the embodiment of FIG. 4 will be described.
The state of D11 shown in FIG. 4 (b) is that the position of the connecting shaft C is in a region (oh) that does not include the door pivot A with the straight line Tv passing through the supporting shafts Sj and Sw at both ends of the spring as a boundary. In the state of D9 shown in FIG. 4C, the position of the connection axis C is in a region (good) including the door pivot O with the straight line Tv as a boundary.
When the position of the connecting shaft C is within the region (oh) that does not include the door pivot A with the straight line Tv as a boundary, the force of the pulling spring V rotates the link A around the connecting shaft C in the direction of the arrow a in the figure. The rotation in the direction of arrow A in the figure is stopped by the contact of the tip of the adjustment bolt Gj1 with the contact Gd when the adjustment bolt Gj1 is attached to the door D, and the position of the connecting shaft C is defined by the straight line Tv as a boundary. When in the region including the pivot axis O (good), the pulling spring V acts to rotate the link A around the connection axis C in the direction opposite to the direction indicated by the arrow A in the figure. The rotation in the opposite direction is stopped when the tip of the adjustment bolt Gj2 comes into contact with the contact Gj when the tip of the adjustment bolt Gj2 is mounted.

The greater the rotation angle Θa about the connection axis C of the link A, the greater the distance Lv between the force action line Tv and the door pivot O. Further, the shorter the distance between the connecting shaft C and the fixed fulcrum Sw, the smaller the change in the length of the tension spring V and the smaller the change in the force of the tension spring V when the link A rotates about the connection axis C. . That is, until the link AJ rotates around the connection axis C in the direction opposite to the arrow A in the drawing and the tip of the adjusting bolt Gj2 comes into contact with Gj, there is almost no decrease in the force of the tension spring V. The acceleration of the door is small and the rotational force acting on the door is increased. The magnitude of the rotational force acting on the door at the time of sealing is determined by the magnitude of “the rotational angle Θa about the connection axis C of the link A” when the tip of the adjustment bolt Gj2 comes into contact with Gj.

In the embodiment of FIG. 2, if the door does not rotate, “the magnitude of the rotational force acting on the door when sealed” does not increase. In the embodiment of FIG. 28, the “magnitude of the rotational force acting on the rotating body when sealed” does not increase unless the rotating body J rotates. On the other hand, the embodiment of FIGS. 3 and 4 does not matter whether the door is rotating or stopped at the time of sealing, the link A rotates around the connection axis C until it hits, and always rotates by a predetermined amount. Force is applied to the door.

The features of the spring mechanism shown in FIGS.
The spring mechanism shown in FIGS. 3 and 4 is characterized in that the link A and the pulling spring V are bent around the connecting shaft Sj as the closing rotation is performed, and the continuous body AV is stored in a small size. There is a feature that the change of the spring length is small through the rotation of the link A, and even when the link A rotates largely, the decrease of the spring force is small, and the magnitude of the spring force can be maintained at the end of the rotation of the link A.
In addition, the spring mechanism shown in FIGS. 3 and 4 can be widely applied in industrial fields other than the door, regardless of the rotation of the door. For example, when the spring mechanism shown in FIGS. 3 and 4 is employed in the copying machine of Patent Document 10, the force for pressing the document can be adjusted to a predetermined magnitude regardless of the thickness of the document.

In the spring mechanism of FIGS. 3 and 4, “the link rotation angle Θd when the link A starts to rotate away from the hit” when the door is closed, and “the link away from the hit” when the closed door is opened. This is different from the rotation angle Θd of the door when A comes into contact again.
The larger the “rotation angle Θa of the link A that rotates away from the hit” when the door is closed, the larger the “rotation angle of the door when the link A starts rotating away from the hit” when the door is closed. From “Θd”, “the rotation angle Θd of the door when the link A away from the contact comes into contact again” when opening the closed door becomes larger.
44 and 45, which will be described later, when the wheel B is attached to the link A and the wheel B moves along the sliding surface K fixed to the door frame W when the door is opened, the link A is reversed. It is configured to be able to rotate, and the “rotation angle Θd of the door when the link A away from the hit comes into contact again” when the closed door is opened is adjusted.

4 (a) to 4 (c), when the tip of the adjusting bolt Gj1 is in contact with the contact Gd attached to the door D, it is in the vicinity of the pivot axis O of the door and the movement support of the pulling spring V on the door side. The axis Sj revolves around the pivot axis O of the door, and the distance Lv between the force action line Tv and the rotation center O is small.
Even if the spring force increases as the door is opened, the rotational force acting on the door is small.
4 (a) to 4 (c), the state where the position of the moving support shaft Sj of the towed point remains in the vicinity of the pivot axis O of the door while the tip of the adjustment bolt Gj1 is in contact with Gd is shown in FIG. 1 is the same as the state in which the connecting axis C of the towed point revolves around the pivot axis O of the door. As described with reference to FIG. 1, the change in the length of the pulling spring V is small in the rotation range (A), and the energy given to the door by the spring is small. Therefore, the maximum door closing speed can be kept low.

As shown in FIG. 4D, the position of the moving support shaft Sj suddenly moves away from the vicinity of the pivot axis O of the door in the rotation range (i). In the state where the tip of the adjustment bolt Gj2 shown in FIG. 4D is in contact with the contact Gj attached to the link A, the distance Lv between the force action line Fv and the rotation center O is large, and the spring is closed when the door is closed. Even if the magnitude of the force is the minimum value, the rotational force acting on the door becomes large.
That is, the force acting on the door is small in the range (A) before the operation of sealing the door starts, and is large in the range (I) after the operation of sealing is started.

As shown in FIG. 4 (a), the distance lgd from the screw Nd to the tip of the adjustment bolt Gjd can be adjusted by turning the adjustment bolt Gjd, and the position of the fulcrum Sj on the door side of the tension spring V is set to the pivot axis O of the door. It can be moved closer to or away from. This makes it possible to adjust the rotational radius of the circular motion around the door pivot axis O of the movement support shaft Sj on the door side of the tension spring V. The force acting on the door can be adjusted within the range of (A).
Further, by adjusting the distance lg1 from the screw N1 to the tip of the adjustment bolt Gj1 by turning the adjustment bolt Gj1, the position of the fulcrum Sj on the door side of the tension spring V can be moved in both the X-axis and Y-axis directions in the figure. In this manner, the “circular motion about the door pivot O of the door side fulcrum Sj” in FIG. 4 can be any one of FIGS.

When the door rotates in the closing direction and shifts from the state shown in FIG. 4B to the state shown in FIG. 4C, the axial center line Zv of the tension spring V crosses the center of rotation C of the link A. As a result, the link A rotates around the connection axis C in the direction opposite to the arrow A in the figure, the tip of the adjustment bolt Gj1 moves away from the contact Gd when it is attached to the door D, and the tip of the adjustment bolt Gj2 moves to the link A. It abuts against the contact Gj.
The “rotational force that causes the pulling spring V to rotate the link A around the connection axis C in the direction opposite to the direction indicated by the arrow“ A ”in the figure gradually increases, and the tip of the adjustment bolt Gj2 is applied to the contact A Maximum when touched. As a result, the link A rotates with time and never rotates instantaneously. This means that it takes time for the latch to hit the door frame W and dent the latch into the door.

Also, when the latch hits the door frame W, the magnitude of the force acting on the door has not reached “the magnitude of the force that dents the latch inside the door”, so the latch remains in contact with the door frame W. It stops and the door stops rotating.
However, when the latch hits the door frame W, as shown in FIG. 4 (c), if the connecting shaft C exceeds the axial center line Zv of the tension spring V, the link A does not matter whether the door is stopped, Rotate around the connection axis C. That is, even if the door is temporarily stopped just before closing, it rotates again and comes into close contact with the door stop.

As shown in FIG. 4B, “the door rotation angle Θd when the connecting shaft C crosses the axis Zv of the pulling spring V at the time of closing” is the position of the fixed fulcrum Sw as “closed door surface D0”. Fine adjustment can be made by moving in the X-axis direction in the figure in parallel. It can also be adjusted by adjusting the “distance lg1 from the screw N1 to the tip of the adjusting bolt Gj1” by turning the adjusting bolt Gj1. The length of the tension spring V changes by moving the position of the fixed fulcrum Sw in the X-axis direction in the figure, but the length of the tension spring V is corrected each time by the turnbuckle TB connected in series to the tension spring V. The
In this way, adjustment can be made so that “rotation of the link A in the direction opposite to the direction of the arrow A in the drawing” starts at the moment when the latch hits the door frame W.

As shown in FIG. 4 (d), “the force that dents the latch inside the door” rotates around the connection axis C of the link A, and the tip of the adjusting bolt Gj 2 hits Gj when it is attached to the rotating body J. The rotation angle Θa of the link A at the time of contact can be finely adjusted by adjusting the “distance lg2 from the screw N2 to the tip of the adjustment bolt Gj2.” As the link A rotates about the connection axis C, the “distance Lv between the force action line Fv and the rotation center O” gradually increases, and the tip of the adjustment bolt Gj2 hits Gj when it is attached to the rotating body J. Maximum when touched. The rotational force acting on the door at this time is the maximum value of “the force to dent the latch inside the door”, and by finely adjusting the maximum value, the force to dent the latch inside the door can be minimized. it can.
In this way, the latch hits the door frame W and dents inside the door, and the operation of the door closely contacting the door is slowed down over time, and the volume of the “click” sound when closing is kept to a minimum. be able to.

When the door is opened from the closed state as shown in FIG. 4D, when the connecting shaft C moves from the region (good) into the region (oh) and crosses the axis Zv of the tension spring V, The link A rotates around the connection axis C in the direction of arrow A in the figure, and the tip of the adjustment bolt Gj1 comes into contact with Gd when it is attached to the door D. When the leading end of the adjustment bolt Gj1 comes into contact with Gd when it is attached to the door D, a state in which “rotation of the link A in the direction opposite to the direction indicated by arrow A” starts at the moment when the latch hits the door frame W Return to. The door D10 in which "the rotation of the link A in the direction opposite to the direction indicated by the arrow A" starts is not shown.
In the process of closing the door as shown in FIG. 4C, the moving support shaft Sj stays close to the door axis O in the state of being close to the door surface, and the connecting shaft C is the axis of the tension spring V. When crossing Zv, the position of the axis of the spring hardly moves, but in the process of opening the door, as shown in FIG. 4 (d), the moving support shaft Sj is rotated with the door while being separated from the door surface. Therefore, the position of the axial center line of the spring moves accordingly. Therefore, “the rotation angle Θd of the door when the connecting shaft C crosses the axis Zv of the pulling spring V” differs between the door closing process and the door opening process, and is larger in the door opening process. That is, in the process of closing the door, the moving support shaft Sj remains close to the door surface until the door rotation angle Θd is almost zero, but in the process of opening the door, Even if the rotation angle Θd increases, the movable support shaft Sj remains separated from the door surface.
When the door is slightly opened and the hand is released from the door while the movable support shaft Sj is separated from the door surface, the spring force acts on the door. In this case, the position where the hand is separated from the door is a state before the moving support shaft Sj is separated from the door surface in the process of closing the door, and is a state where there is no force to seal the door. That is, even when the hand is released from the door at the “position where there is no force to seal the door” in the process of closing the door, the door is sealed. In addition, in the process of closing the door, even if the door does not have the force to rotate the door and the door continues to rotate only with inertial force, No matter where you open the door and move your hand away from the door, it will not stop.

FIG. 5 is an embodiment of the closing device described in FIG. 4, FIG. 5 (a) is a plan view showing a closed state, and FIG. 5 (b) is a figure and an elevation view. FIG. 5C is an elevational view showing a state where the door is slightly opened.
Since the link A wraps around the tension spring V and is also a structural member having the moving support shaft Sj at the tip, the position and operating range of the link A are above the door upper end XX that does not hit the door, and the tension spring V, The link A and the moving support shaft Sj move circularly in a horizontal plane above the door.
The link A is a box-shaped member having a cross-section of a piece, and the butterfly plate Ad is attached to the lower side surface, the butterfly plate Ad is attached to the door, and the rotation axis of the butterfly plate Ad is the connecting shaft C shown in FIG. Therefore, the link A revolves around the pivot axis O of the door while swinging about the connection axis C.
Further, the hinge Ad is fitted with Gj1 and Gj2, and the opening / closing range of the hinge Ad is limited.

In FIG. 6, the distance (Lbo or Lbc) between the vector of the force (Fb) and the rotation axis (O or C) for the rotating body (D) rotatably supported around the rotation axis (O in FIG. 6). ) Changes and the rotational force (Mc) acting around the center of rotation (C) or the force (Fb) changes, or the sliding surface K (K in FIG. 19) changes. For the moving wheel (Bb), the vector of the force (F in FIG. 19) acting in the moving direction of the wheel (Bb) is converted into two component forces (Fd, Fb) having different sizes and directions. A switchgear characterized by comprising a change.

In FIG. 6, the rotational force (Mc) acting around the rotation center (C) is the product of the force (Fb) and the “distance between the force (Fb) vector and the rotation center (C) (Lbc)”. Since (Mc = Fb * Lbc), Lbc becomes smaller and Fb becomes larger. Since ((Mo = Fb * Lbo)), Lbc increases and Mo increases.
When the center of rotation is the pivot axis O of the door and the rotating body is the door D, “a position close to the rotating axis O (the force Fb acts on Lb100 to rotate the rotating body D”) ”, A“ rotating means in the range of (ii) ”and a“ rotating means in the range of (a) ”or“ (ii) in which a force acts on a position (Lb0) far from the rotational axis to rotate the rotating body ”. An opening / closing device comprising “switching means” for switching to “rotating means in the range of
When the center of rotation is the connecting shaft C and the rotating body is the link A, “the rotating means within the range (A) where the rotating body A rotates and a force is applied to a position (Lbc100) far from the rotating shaft” , Switching between “rotating means in the range of (ii)” and “rotating means in the range of (a)” or “rotating means in the range of (ii)” where the force acts at a position (Lbc0) close to the rotation axis. An opening / closing device comprising “switching means”. "
Other embodiments of the latter are shown in FIGS.

FIG. 6 is an “opening / closing device having a continuous track at a position far from the position close to the rotation axis”, and the vector of the force (Fb) moves as the wheel B moves.
Alternatively, the closing device can be attached to “one mounting shaft provided near the driven shaft” and “the other mounting shaft provided at a position far from the driven shaft”. One is attached to the driven rotating body, the other is attached to the fixed portion, the one mounting shaft is movably attached to the driven rotating body or the fixed portion, and the position of the one mounting shaft is set to the driven shaft. Is a closing device provided with a releasable restraining means that can be moved to a position far from the driven shaft by being restrained in the vicinity of the shaft and released from the restraint, and other embodiments of this device are shown in FIGS.

Other embodiments are shown in FIGS. 10 to 12 and FIGS. 14 to 22, “Equipped with the door stop for preventing rotation of one of the driven rotary bodies, and the driven rotary body at a position close to the driven shaft as an action point of force. And a sealing device for bringing the driven rotary body into close contact with the door stop using a position far from the driven shaft as an action point of force, and from the rotating device to the sealing device, or An opening / closing device for switching from a sealing device to the rotating device, comprising a releasable restraining means for restraining movement of the action point.

For example, in FIG. 6, the slide body K is attached to the fixed portion, and the link A is connected to the fixed portion (W), which is connected between the rotating body (D) and the fixed portion (W). In FIG. 15, the link A is attached to the fixed portion, and the sliding body K is attached to the driven rotating body D.
The sliding surface is fixed to the link.
“With a structure including a wheel, a sliding surface that moves along with the wheel, and a sliding body that includes the sliding surface, one of the wheel and the sliding body is attached to the drive rotating body, and the other is attached to the fixed portion. An opening / closing device in which the wheel presses the sliding surface while moving along the sliding surface to bring the driven rotating body into close contact with the door stop, and the driven rotating body is moved to the door An opening / closing apparatus characterized in that the direction of the line of action of the force that comes into close contact with each other is substantially perpendicular to the axis of the driven rotor. "

"Link device for connecting the rotating body (D) and the fixing portion (W) with two links (J, A,)" The sliding surface fixed to the link shown in FIGS. In (f), the door D is rotatably attached. One of the two adjacent links is a link having a sliding surface K, and the sliding body K. FIG. 57 (f) shows two adjacent links (A and D sliding bodies are attached to the driven rotating body and driven. The shaft is attached to the fixed portion, and the wheel B does not detach from the sliding surface K as shown in FIG.

Generally, the biasing means of the opening / closing device is attached to a position near and far from the driven shaft, and the sliding surface on which the mounting shaft near the driven shaft moves moves from a position near to the far side from the driven shaft. A releasable restraining means for allowing the slider to stay at a position close to the driven shaft of the passage or move to a position far along the passage; The crossing angle between the straight line passing through the rotating shaft and the sliding surface is changed by the rotation of the driven shaft, and stays at a position close to the driven shaft with a predetermined opening of the driven rotating body as a boundary. An opening / closing device, wherein the slider is moved to a position far from the driven shaft.

6-8, the wheel B moves along the sliding surface K provided in the vicinity of the pivot O of the door, the wheel B presses the sliding surface K, and the door is centered on the pivot O of the door. It is a top view explaining operation | movement of the Example made to rotate to the arrow B direction in the figure, Comprising: As the wheel B moves, "the action line of the force Fb which the wheel B presses the sliding surface K" and the door This is an embodiment in which the distance Lf to the pivot O changes and the magnitude of the moment M of the force acting around the door pivot O changes.
The line of action of the force for rotating the door is a straight line Fb passing through the “contact point b between the wheel B and the sliding surface K” and the rotation axis Ib of the wheel, as shown in FIG. 6B.

In FIGS. 6 and 7 (a), D100 indicated by a solid line indicates a fully open state, and D0 indicated by a solid line in FIGS. 6 and 7 (b) indicates a closed state. A, V, C, B, and Ib illustrated in a plurality of locations indicate positions where the link A, the pulling spring V, the connection shaft C, the wheel B, and the wheel rotation shaft Ib have moved as the door rotates, respectively. , V, C, B, and Ib correspond to the subscripts of the door D and correspond to the respective rotation angles of the door D (door opening Θd).
In FIG. 6, the link A is centered on the connecting axis C, and in FIGS. 7 and 8, the rotating body J is rotated about the connecting axis C by the force of the pulling spring V. The spring that rotates the link A or the rotating body J is The spring is not limited to a tension spring, and may be a push spring, a torsion spring, or another spring.

6 and 7, a wheel rotation axis Ib is provided at the tip of the link A, and a wheel B is mounted on the wheel rotation axis Ib.
In FIG. 6, the wheel B tries to revolve around the connecting shaft C, and the revolution is “sliding surface K as shown in FIG. 6 (a)” in the “range from fully open to immediately before closing (A)”. In the “range from just before closing to the closing time (i)”, as shown in FIG. ,
The crossing angle between the direction in which the wheel B tries to move and the sliding surface K changes with the rotation of the door, and the closer to the right angle the moving direction of the wheel B and the sliding surface K, the harder the wheel moves. However, as the link A and the sliding surface K are closer to each other, the rotational force acting around the connection axis C acts in the direction of rotating the door, and the force is not transmitted in the axial direction of the link A. Also, the closer to parallel, the easier it is to move, but the closer the link A and sliding surface K are to a right angle, the smaller the rotational force acting around the connection axis C is, and the smaller the force that rotates the door, is transmitted in the axial direction of the link A. Power increases.

Rc10 shown in FIG. 6B is a circle whose radius is the distance between the “contact point b10 between the wheel B10 and the sliding surface K” and the connection axis C10 and centered on the connection axis C10. This is a distance between the “contact point b0 between the wheel B0 and the sliding surface K” and the connection axis C0, and is a circle centered on the connection axis C0.
The sliding surface K is a circle centered on a point C5 located farther from the “closed door surface D0” than the point C0. It is a point in position. A circle O is a circular orbit of the connecting axis C around the pivot axis O of the door. Rci (i = 0,5,10, ...) has a radius "contact point bi (i = 0,5,10) between the wheel Bi (i = 0,5,10, ...) and the sliding surface K. , ...) "and the connection axis Ci (i = 0,5,10, ...) and a circle centering on the connection axis Ci (i = 0,5,10, ...) Then, in the “range from fully open to just before closing (A)”, the circumferential portion after the intersection b of the circle Rci is outside the sliding surface K, and the wheel B is slightly along the sliding surface K. The connection axis C approaches C5 while moving and rotating the door D. As the connection axis C approaches C5, Rci approaches the sliding surface K, and the circumferential portion after the intersection b moves from the outside to the inside with the boundary when the connection axis C is at the position C5.

In FIG. 6B, the wheel B10 is urged by the pulling spring V along the sliding surface K in the direction indicated by the arrow C in the figure, and the circle Rc10 extends from the position of the contact b10 in the direction indicated by the arrow C in the figure. Being outside the circle, the movement of the wheel B in the direction of arrow C in the figure is prevented.
6A is also prevented from moving in the direction indicated by the arrow C in the drawing, and the wheel B 100 in the direction indicated by the arrow C in the “rotational range before starting the sealing operation (A)”. The movement is blocked by the sliding surface K. The wheel B moves when the door D closes and rotates in the direction of arrow B in the figure. 6B, the circle Rc0 is inside the circle of the sliding surface K from the position of the contact b0 in the direction opposite to the arrow C in the figure, and the movement of the wheel B in the direction of the arrow C is blocked by the sliding surface K. However, the wheel B moves when the door D rotates in the opening direction opposite to the arrow B in the figure.
In the case of FIG. 7, the force with which the wheel B presses the sliding surface K, that is, “the straight line Fb passing through the contact point b between the wheel B and the sliding surface K and the rotational axis Ib of the wheel” is closer to the sliding surface K. The wheel is easy to move, and the closer to parallel, the harder it is to move.
FIGS. 6 to 8 show that the wheel is difficult to move in the “range from fully open to just before closing (A)”, and slides so as to be easy to move in the “range from just before closing to the time of closing (Yes)”. The gradient of the surface K is changed, and the wheels are suddenly moved by a slight rotation of the door when the door is sealed.
“The point of action of the force acting around the rotation axis” has a passage that moves from a position very close to the rotation axis to a position far from the rotation axis. By approaching, the force is reduced to the infinite prize and transmitted, and the ratio of the force transmitted when it is very close to the rotation axis and the force transmitted when it is far away is infinite, so the magnitude of the force transmitted to the rotating body A big difference is provided.
There is a difference between whether or not the rotational force required when sealing the door is added to the rotational force required before that, and the world handled by addition or subtraction. The device is intended to be made smaller by handling it by the multiplication / division of the ratio of the force transmitted when it is very close to the axis and the force transmitted when it is far away.
By approaching the "acting point of the force acting around the rotation axis" very close to the position, the force is reduced to infinity and transmitted, and when transmitted at a position very close to the rotation axis, By making the ratio of infinite, the greater the angle of intersection between the circular track R and the sliding surface K, the more the rotational force acting around the door pivot O will work in the direction of rotation of the door. The force that pushes the sliding surface K works in the direction of the line of rotation, but the shape of the sliding surface K matches the shape of the sliding surface K that works more effectively in the direction of rotating the door, and the “switching means” starts. To do.

6 and 7 as well as in FIGS. 34 and 36, the tangent line T of the sliding surface K passing through the “contact point b between the wheel B and the sliding surface K” and the link A as shown in FIG. The movement is started when the obtuse angle is obtained when the moving direction side of the wheel B is 90 degrees at the intersection angle with the axis axis Za. In other words, the crossing angle between the tangent line T of the sliding surface K passing through the “contact point b between the wheel B and the sliding surface K” and the axis core line Za of the link A moves toward the obtuse angle side. Does not move toward the acute angle side. In the case of FIG. 34 in which the compressive force acts on the link A and in the case of FIG. 36 in which the tensile force acts, the crossing angle moves toward the obtuse angle side.

In the “range from fully open to just before closing (A)”, the wheel moves little and the door rotates greatly. Therefore, there is little acceleration of the door. In the “range from just before closing to the time of closing (i)”, the movement of the wheel is large and the door rotates small. Therefore, the acceleration of the door is great. The acceleration of the door is limited to a slight rotation of the door when the door is sealed, so that the angle at which the door rotates is made as small as possible by moving the wheel suddenly, or the damper described later is moved "the wheel suddenly moves. The acceleration of the door is reduced by working effectively only when. In order to reduce the impact sound at the time of sealing, the spring force acting at the time of sealing is made as small as possible so that the latch is barely recessed in the door.

The force to seal the door can be increased by increasing the spring force, but it is no exaggeration to say that the door will rotate unless the force to rotate the door is zero. If the force that rotates the door is made as small as possible, the ratio of the force that seals the door to the force that rotates the door increases, which solves the problem of "slowly rotating with a small force and sealing tightly with a large force". However, as described above, if it is tightly sealed with a large force, it will accelerate when sealed and the impact sound will increase, so make sure to rotate slowly with a small force and seal with a force that is not larger than necessary. It is desirable to be able to adjust the rotating force and the door sealing force separately.
As shown in FIGS. 2 to 8, it is a device for processing “work for rotating the door” and “work for sealing the door”, and it is not a device for processing with one spring. A device consisting of two devices relayed from "rotating device" to "door sealing device", and a device that processes with separate springs, and can adjust the force to rotate the door and the force to seal the door separately. It is desirable to do so.

The “distance Lf between the line of action of the force Fb and the pivot O of the door” in the embodiment shown in FIGS.
FIGS. 6 and 7 (a) show a series of operations of “the rotation range before the start of the sealing operation (A)” from the fully open state to the closed state, and in the case of FIG. In the case of FIG. 7, the wheel B is kept stationary at the end K0 of the sliding surface K closer to the pivot O of the door. In both the case of FIG. 6 and FIG. 7, the wheel B is fastened to the end K0 of the sliding surface K closer to the door pivot O, thereby “the distance Lf between the line of action of the force Fb and the door pivot O”. The door is closed and rotated slowly with a weak force.
FIGS. 6 and 7 (b) show a series of operations of “the rotation range after the start of the sealing operation (i)”. When the sealing operation starts in both FIG. 6 and FIG. As the distance Lf suddenly increases during the sealing operation, the door is sealed with a large force.
The force Fb that the wheel B presses the sliding surface K is generated for the first time when the link device is stationary and balances structurally and does not move. Since the door D is prevented from rotating by a door stop (not shown), the sealing force Works great.

In the switching range of the boundary between the rotation range (A) shown in FIGS. 6 and 7 (a) and the rotation range (I) shown in FIGS. 6 and 7 (b), the wheel B moves greatly on the sliding surface K. As a result, the force of the spring decreases, and even if the “distance Lf between the line of action of the force Fb and the door pivot O” is increased, the force Fb may not grow to a force sufficient to seal the door. .
By bringing one of the springs closer to the connecting shaft C which is the center of rotation of the rotating body J in FIG. 7 of the link A in FIG. Although there is a measure to reduce the decrease in the distance, the link A in FIG. 6 acts on the rotating body J in FIG. Measures are taken to reduce the power to a large force Fb. In this way, the magnitude of the force Fb acting on the door itself is increased, and the action point at which the force Fb acts on the door D is moved away from the door pivot O so that a large sealing force acts at the end of the rotation. become.

6 and 7, the wheel B is attached to the rotation axis Ib of the wheel provided at the front end of the link A, and the closer the wheel B is to the pivot O of the door, that is, the end of the sliding surface K is closer. The closer to the door pivot O, the smaller the “distance Lbo between the action line of the force Fb and the door pivot O”, and the ratio of the force for sealing the door to the force for rotating the door increases.
As the “distance Lbo between the line of action of the force Fb and the pivot axis O of the door” approaches zero, the ratio of the force for sealing the door to the force for rotating the door approaches infinity.
Further, the rotational force M acting around the connecting shaft C at the time of sealing is balanced with the force Fb that the wheel B presses the sliding surface K, and the “distance Lbc between the force action line Fb and the center of rotation C0” is zero. As it approaches, the force Fb approaches infinity.
The means for allowing two different forces to act on the closing device is a means for changing the “distance between the action line of the force acting around the rotation axis and the rotation axis”. There is a case where the force is reduced and a case where the working force is increased as in the latter, and both means are effective as shown in FIG. Make two different forces work.

The structure of the embodiment of FIG. 6 and the operation of the switching means will be described.
In FIG. 6, the link A is rotatably supported around a connecting shaft C provided on the door D, and is urged by a pulling spring V in the direction of arrow A in the figure. As shown in FIG. 6 (a), in the "rotation range before the start of the sealing operation (A)", the rotation of the link A in the direction of arrow A in the drawing is blocked by the sliding surface K, and the wheel B is in the sliding surface. Pressing K causes the door D to rotate and close in the direction of arrow B in the figure. The link A rotates when the door D is closed and rotated in the direction of arrow B in the figure.
When the sealing operation is started as shown in FIG. 6B, the rotation of the wheel B in the direction of arrow A in the drawing is not prevented by the sliding surface K, and when the door rotates slightly in the closing direction, the wheel B The sliding surface K moves to the end Ke far from the door pivot O.

The impact sound is the smallest when the force that acts when sealing is necessary and sufficient. At the end of the range (A), the pulling spring V has no “force to dent the latch that is in contact with the door frame W”, so that when the latch contacts the door frame W, the door stops and the link A also stops. However, if the connecting shaft C is attached to the rotating body Jc pivotally supported by the connecting shaft Cj provided on the door and is movable, the rotating body can be used even if it is less than the "force to dent the latch that contacts the door frame W". Jc can rotate, and the link A rotates and the wheel B reaches the end Ke of the sliding surface K, so that the force acting on the door becomes necessary and sufficient.

The structure and operation of the embodiment of FIG. 7 will be described.
In FIG. 7, the rotating body J is rotatably supported around a connecting shaft C provided on the door D, and the link A is connected to a connecting shaft P provided at the tip of the rotating body J. The pulling spring V connects the support shaft Sd provided on the door D and V supports the support shaft Sj provided on the rotating body J, and the wheel B presses the sliding surface K in the axial direction of the link A by the pulling spring V. Then, the door D is closed and rotated about the pivot axis O of the door in the direction of the arrow B in the figure. 7 is a crank mechanism that converts the “circular motion of the connecting shaft P of the rotating body J” into the linear reciprocating motion of the working body link A.
As shown in FIG. 7A, in the “rotation range before the sealing operation starts (A)”, the wheel B is stopped at the end K0 of the sliding surface K near the door pivot O, When K0 is the concave surface of the arc, the line of action of the force that the wheel B presses the sliding surface K is directed to the focal point of the concave surface of the arc, and when the concave surface of the arc coincides with the outer periphery of the wheel B, Overlap. When the end K0 is “a concave surface of an arc that coincides with the outer periphery of the wheel B” or when the end K0 supports the wheel B at two points, the wheel B stops at the end K0.

In the entire process from when the door is fully opened to when it is closed, the connecting axis C moves on the circumference Ro centered on the door pivot axis O, and the connecting axis P moves on the circumference Rib10 centered on the wheel rotation axis Ib10. To do.
Here, since the distance between the rotating shaft Ib of the stationary wheel and the connecting shaft C continues to decrease, the rotating body J continues to rotate around the connecting shaft C in the direction indicated by the arrow A in the figure.

The line of action of the force Fb at which the wheel B presses the sliding surface K is on a straight line passing through the “contact point B between the wheel B and the sliding surface K” and the rotational axis Ib of the wheel. The distance from the pivot axis O increases slightly. The decrease in the magnitude of the spring force Fb is smaller as the length of the spring is longer and the distance between the support shaft Sj and the door pivot O is smaller, so the moment of force around the door pivot O acting on the door is constant. Can be made.

When the sealing operation is started as shown in FIG. 7B, if the crossing angle with a exceeds 90 degrees with respect to the linear portion between the end K0 and the end Ke of the sliding surface K, the wheel B moves along the straight portion of the sliding surface K in the direction of the arrow C in the figure.
Here, the straight line portion between the end K0 and the end Ke of the sliding surface K is the connecting shaft when the wheel B is at the end K0 of the sliding surface K and starts to move in the direction of arrow C in the figure. If it approximates to a circle whose center is the position of P and whose radius is “the distance between the contact point b of the wheel B and the sliding surface K”, the change in the length of the spring when the wheel B moves to the end Ke There is little decrease in spring force. In the first place, when the wheel B starts to move in the direction indicated by the arrow C in the figure, the crossing angle between the sliding surface K and the link A is 90 degrees. Since the surface K approximates the circle, there is little change in the length of the spring, and there is little decrease in the spring force. If the moving distance on the sliding surface K of the wheel B is long, the change of the spring length is large and the decrease of the spring force is large, but the distance Lf between the link A and the pivot axis O of the door becomes large, The moment of force around the door pivot O is increased.

Further, the rotational force acting around the connection axis C when sealed is balanced with the force Fb that the wheel B presses the sliding surface K, and the “distance Lbc between the force action line Fb and the rotation center C0” approaches zero. Then, the force Fb at which the wheel B presses the sliding surface K approaches infinity. That is, the force Fb at which the wheel B presses the sliding surface K increases as the axial center line of the link A and the rotating body J approaches a straight line.
The force Fb by which the wheel B presses the sliding surface K is generated only when the link device is stationary and does not move in balance with the structural mechanics. If the door D is not prevented from rotating by a door stop (not shown), the sealing force Will not grow.

FIG. 8 is an embodiment of the closing device described with reference to FIG. 7. FIG. 8A is a plan view showing a closed state, and FIG. 8B is an elevational view. FIG. 8C is an elevational view showing a state where the door is slightly opened.
The link A is a box-shaped member having a U-section and wraps and hides the pulling spring V and the rotating body J and accommodates them inside. At the same time, it is also a structural member that attaches the wheel B to the tip and rotates about the connecting shaft P. In the case of FIG. 8, since the sliding surface K is attached below the door upper end XX of the vertical member Wv of the door frame W, the position and operating range of the link A are below the door upper end XX. The link A and the rotating body J move in a horizontal plane below the door upper end XX.

In the closing device described in FIG. 7, the wheel B instantaneously moves from one end of the sliding surface K to the other end immediately before closing, and the wheel B collided with the end of the sliding surface K. An impact sound is generated. FIG. 8 (a) shows the structure of the sliding surface K in a cross-sectional view. A buffer Kd such as rubber is interposed between the mounting portion Kb of the sliding surface K and the presser Ka so that the sliding surface K The impact sound at the time of collision is softened by covering the end with the buffer Kd. The presser Ka is fixed to the mounting portion Kb with a bolt Kc with the buffer Kd interposed therebetween. The presser Ka is a linear portion of the sliding surface K and is a sliding surface of the wheel B.

FIG. 9 shows a rotating mechanism for stopping the door at the end stage of “range from fully open to just before closing (A)”. FIGS. 9A and 9C show the spring 1 as in FIG. 9 (b) and 9 (d) have the same structure as that of FIG. 7, and a link A connects the rotating body J operating at a position away from the door pivot O and the vicinity of the door pivot O. It connects with.

Many of the present applications are devices that seal the door by the rotation of the rotating body J as shown in FIGS. 9B and 9D, and many are not shown in the rotating body J shown in FIGS. 9B and 9D. A wheel B "that presses the sliding surface K is mounted. 19 and 20 is an apparatus that seals the door not by the rotation of the rotating body J but by the shaft Sf that moves in the axial direction of the through hole Sh.
By providing the rotary body J at a position away from the door pivot axis O, the point of action of the force for sealing the door is set at a position away from the door pivot axis O. ”And a supporting shaft in the vicinity of the pivot axis O of the door, a force for rotating the door is applied to the supporting shaft in the vicinity of the pivot axis O of the door.
In the embodiment of FIGS. 2 to 8, through the process of sealing from the process of rotating the door, “the point of action of the force acting on the door moves on a continuous track, and one point of action of the pivot axis O of the door In many embodiments described below, the point of action moves discontinuously from a position close to the door pivot O to a position far away. The two action points act separately at positions near and far away from the door pivot axis O, respectively.

9 to 22 includes a door frame W (fixed portion) and a door D (driven rotating body) that rotates about a pivot O (driven body rotating shaft) of a door provided on the door frame W. And a connecting shaft C provided on the door D and a fixed support shaft Sw provided on the door frame W (fixed portion) by a biasing means, and a rotational force acting on the door D (driven rotating body) "Rotating means in the range of (A)" with a small "Rotating means in the range of (I)" and the force acting on the door D (driven rotating body) is changed from main to large or from large to small. The switching device includes a switching means, and the “rotating means in the range (A)” and the “rotating means in the range (I)” work around the pivot axis O (driven body rotational axis) of the door. A change in the distance between the line of action of the force and the center of rotation changes the rotational force acting around the door pivot O (driven body rotation axis), or the door pivot. A means for making the force acting on the door D (driven rotating body) two different magnitudes by changing the magnitude of the force acting around the (driven body rotating shaft). An opening / closing device comprising releasable restraining means for restraining a distance between the line of action and the center of rotation.
Speaking of an opening / closing device in which the rotational force acting around the pivot axis O (driven body rotating shaft) changes, as means for making the forces acting on the door D (driven rotating body) two different magnitudes, FIG. In the eighth embodiment, one of the connection shaft C and the fixed support shaft Sw, which are the support shafts at both ends of the urging means, is provided at a position close to the door pivot O (driven member rotation shaft), and the other is provided at a position far from it. The support shaft provided at a position close to the door pivot axis O (driven body rotation axis) is movably attached along a path continuing from a position near the door pivot axis O (driven body rotation axis). A support shaft provided at a position close to the door pivot O (driven body rotating shaft) is constrained to a position near the door pivot O (driven body rotating shaft), and the restraint is released to move to a far position. An opening / closing device comprising a restraining means.
Even if the support shaft provided at a position far from the pivot axis O (driven body rotation shaft) of the door is moved, the change in the distance between the force action line and the center of rotation is small, and the support shaft provided at a close position is required. Move.
However, if the movement of the support shaft provided at a position close to the pivot axis O (driven body rotation axis) of the door is limited to a passage continuing from a close position to a position far from the close position, the distance between the force action line and the center of rotation is There is a limit to the size, and there are means for discontinuously moving the line of action of the force so as to have two different sizes as shown in FIGS. FIG. 13 shows one of means for making two different magnitudes by changing the magnitude of the force acting around the pivot axis O (driven body rotation axis) of the door.

“A structure in which a support shaft at a position close to the door pivot O and a support shaft at a position far from the door pivot O are connected by a connecting rod via a biasing means and a releasable restraining means”. The bar is link A in the figure.
In the embodiment of FIGS. 2 to 8, the link A rotates with the support shaft at a position far from the door pivot O as the rotation axis, and the tip opposite to the rotation axis acts in the vicinity of the door pivot O. The point moves from a position close to the door pivot axis O to a position far away, and increases the “distance between the line of force acting on the door and the door pivot axis O”. In order to increase the "distance between the line of force acting on the door and the pivot axis O of the door", the tip must be moved greatly or the link length must be increased. Don't be. As a result, the apparatus becomes large.
On the other hand, in the other embodiments, the link A is connected to the "sealing device separated from the door pivot O" in appearance, and the link A connects the sealing device and the support shaft in the vicinity of the door pivot O. The “sealing device apart from the door pivot O” also has a function of rotating the door. The link A performs a substantially linear reciprocating motion and has a small operating range. As a result, the size of the device is reduced, and when the door is closed, the device is stored in a small box.

In FIG. 1, when the axis of the spring and the center of rotation O of the door are in a straight line, the rotation of the door stops. In FIGS. 6 to 8, the straight line passing through the rotation axis Ib of the wheel and the contact b is “acting on the door. When the action line of force is in line with the pivot axis O of the door, the door stops. Also in FIG. 9, the line of action of the force, that is, when the axis of the tension spring V in FIGS. 9 (a) and 9 (c) and the axis of the link A in FIGS. 9 (b) and 9 (d) pass through the pivot axis O of the door. The door stops.
In FIG. 9, the “force acting on the door” is the vector sum of the component force in the axial direction of the door axis and the component force perpendicular thereto, and the “action line of the force acting on the door” is separated from the door door shaft axis. As the overlapping state approaches, the former increases and the latter decreases. The former is a force applied to the door pivot O, and the rotational resistance around the door pivot O increases. The latter is a force for rotating the door, and the rotation speed of the door is reduced.
The door stops when the line of force action passes through the door pivot O, but does not stop even if the rotational force acting on the door is small when passing near the door pivot O. In ordinary doors, the maximum static frictional force is small, and the door does not stop except when the line of action of the force passes through the pivot axis O of the door.
As shown in FIGS. 1 to 5 and 6 to 8, “the line of force acting on the door” is applied to the pivot axis O of the door immediately before closing at the end stage of “range from fully open to just before closing (A)”. When approaching, the door will move to a stop state due to insufficient force to rotate the door and decelerate. When the acting line of the acting force moves away from the door pivot axis O, it does not approach the stop state and does not decelerate.
In the case of FIGS. 1-5, the door is pulled and rotated, and in the case of FIGS. 6-8, the door is pressed and rotated.

FIG. 9 shows an embodiment in which the door stops immediately before closing, but even when the door stops, the switchgear must continue to operate without stopping and be relayed from the rotating device to the sealing device.
When the rotation of the drive unit and the rotation of the driven unit are directly connected as in the rotation transmission mechanism of FIGS. 9B and 9D, the rotation of the drive unit stops when the rotation of the driven unit stops. The rotation transmission mechanism of FIGS. 9B and 9D is a link device including four links, that is, a door frame W, a door D, a link A, and a rotating body J. When passing, the door D and the link A overlap with each other so that the link device does not deform, and the link device does not move.
10 to 12 show an embodiment in which the rotation of the drive unit is not stopped even when the door is stopped. Immediately before closing, the link device becomes the above-mentioned triangle that does not move, but when the length of one of the links changes, it becomes rotatable and relays from the rotation device to the sealing device. In FIGS. 14 to 18, one of the links constituting the link device is used as a spring, so that the above-described triangular link device that does not move can be rotated and relayed from the rotation device to the sealing device.
In FIGS. 19 to 22, the sealing device is made rotatable so that the “switching means” does not relate to the rotation of the door. The rotation transmission mechanism in FIGS. 1 to 22 is such that one opening / closing device functions as both a rotating device and a sealing device, but in FIGS. 24 to 27, the rotating device and the sealing device are prepared separately and function respectively. However, as shown in FIG. 1 (d), in the embodiment in which the force for starting the sealing device remains in the rotating device at the end stage of “range from fully opened to immediately before closing (A)”. As the rotating device does the work of starting the sealing device, the door slows down and relays from the rotating device to the sealing device without stopping.

10 to 12 and FIGS. 14 to 21, the wheel B enters the sliding surface K <b> 1 immediately before closing, presses the sliding surface K <b> 2, and the wheel B presses the sliding surface K. The door is hermetically sealed. Further, when the door is opened, the wheel B is separated from the sliding surface K, and the wheel B and the sliding surface K are repeatedly contacted and separated, but the rotating body J that drives the wheel B rotates independently of the door. Therefore, there is no one-to-one correspondence between the rotation angle of the door and the operation of the sealing device, and the position at which the wheel B contacts the sliding surface and the position at which the wheel B separates are not always constant. Also, between the slight rotation angle of the door just before closing, the magnitude of the inertial force attached to the door and the magnitude of the rolling friction of the wheel B are different, and the start timing and motion speed of the wheel B vary, and the door is sealed. When the door is opened and when the closing device is restored, the door is rotated and slightly displaced.
23 to 27, since the drive shaft and the pivot of the door are directly connected, the rotation of the drive shaft and the rotation of the door have a one-to-one correspondence, and the embodiments of FIGS. In these embodiments, the wheel B and the sliding surface K continue to come into contact with each other and do not separate. Therefore, in these embodiments, when the door is sealed and when the door is opened and the closing device is restored, the door rotates and shifts. Absent.
10 to 12 and 14 to 21, the rotating device is insulated when the sealing device is operated. In the embodiments of FIGS. 23 to 27, 46 and 49, the rotating device maintains a relationship with the rotation of the door until the door is closed, so that there are few accidents in the relay from the rotating device to the sealing device.
These are different in structure, but are common in that “the force acting on the door acts strongly at the end of the closing rotation”. Various closing devices can be considered in which the force acting on the door follows the same process, but a closing device with a complicated structure is meaningless and cannot be adopted. The closing device shown in the present application is a simple closing device selected from among the closing devices that satisfy the problem that “the force acting on the door acts strongly at the end of the closing rotation”.

FIGS. 10 to 12 FIGS. 14 to 18 The sealing devices illustrated in FIGS. 24 to 27 are designed to be sealed with as much force as possible with the force of a spring as small as possible. The stronger the direction of the force with which the wheel B presses the sliding surface K is perpendicular to the closed door surface, the stronger the stronger the sliding surface K is in parallel with the closed door surface. The wheel B moves parallel to the closed door surface and presses the sliding surface K at a right angle.
The sliding surface K slides with the wheel B landing at the end of the “range from fully open to just before closing (A)” or at the beginning of “range from just before closing to when closing (yes)”. The sliding surface K1 is substantially perpendicular to the closed door, and the pressing surface K2 is substantially parallel to the door that is pressed and closed when sealed. When the latch is about to be recessed, the wheel B moves along the pressing surface K2, which is substantially parallel to the door, with little resistance. During sealing, the wheel B moves on the pressing surface K2, which is easy to move and generates a strong sealing force.
Further, in order to facilitate the movement of the wheel B even with a weak spring force, a wheel having a small rotational resistance, such as a wheel equipped with a bearing, is adopted as the wheel B.

The line of action of the force that seals the door is the straight line Fb that passes through the “contact point b between the wheel B and the sliding surface K” and the rotation axis Ib of the wheel, but the point where the reaction force of this force is generated does not move. Only on the spot does it act strongly on the door.
10 and 11, the point at which the reaction force of the “force that is a straight line Fb passing through the contact point b between the wheel B and the sliding surface K and the rotation axis Ib of the wheel” is generated is fixed. On the sliding surface K, this force pushes the door against the door.
In the embodiment of FIG. 12, as shown in FIG. 12 (d), a reaction force of “force whose line of action is a straight line Fb passing through the contact point b between the wheel B and the sliding surface K and the wheel rotation axis Ib” is generated. The rotating shaft Sw of the rotating body J is fixed, and this force presses the sliding surface K attached to the door and presses the door against the door.

The stronger the force pressing the door against the door at the time of sealing, the greater the force required to open the closed door, but the wheel B presses the sliding surface K in the embodiment of FIGS. When the direction of the force is perpendicular to the closed door surface, when the action line of the force that the wheel B presses the sliding surface K passes through the rotation axis Sw of the rotating body J in the embodiment of FIG. I can't open it.
For this reason, in the embodiment of FIGS. 10 and 11, the wheel B in the embodiment of FIG. 12 is not slightly perpendicular to the closed door surface in the direction in which the wheel B presses the sliding surface K. The line of action of the force that presses the sliding surface K is slightly separated from the rotational axis Sw of the rotating body J.

10 to 12 show a “sealing device in which the revolving wheel B moves along the sliding surface K”. In FIGS. 10 and 11, the sliding surface K and the wheel B are interchanged to slide on the door D. The surface K rotates and moves along the wheel B fixed to the door frame W. In FIG. 12, the sliding support shaft Sw fixed to the door frame W is replaced by replacing the sliding surface K and the wheel B. A sealing device in which the sliding surface K rotates at the center and moves along the wheel B attached to the door, that is, a “sealing device in which the revolving sliding surface K moves along the wheel B” is also conceivable. An example of FIG. 45 described later is a “sealing device in which the revolving sliding surface K moves along the wheel B”.

In FIG. 1, when the force of the spring is as close to 0 as possible, the rotational force acting on the door balances the frictional resistance and the air resistance of the pivot axis O of the door, and the rotation of the door is explained as a constant speed motion. It has been explained that the rotation of the door stops when the tow point, the towed point, and the rotation center O of the door are in a straight line. In FIG. 9, even when the rotation of the door is accelerated, the case where the rotation of the door is stopped just before the door is closed will be described.
9 (a) and 9 (c), a connecting shaft C provided on the door D and a fixed fulcrum Sw fixed to the door frame W are connected by a pulling spring V, and the door D is shown with an arrow O in the figure about the pivot axis O of the door. The door rotates toward the straight line Ts even at (a) and (b) with “the straight line Ts passing through the door pivot O and the fixed fulcrum Sw” as a boundary. The “distance between the connecting shaft C and the fixed fulcrum Sw” is the smallest, and the door is stationary when the axial center line of the tension spring V is on the straight line Ts.
This state is the state described with reference to FIG. 1 "the rotation of the door stops when the towing point, the towed point, and the rotation center O of the door are in a straight line".

FIG. 9B shows a rotating body in which a connecting shaft P provided at the tip of a rotating body J that rotates about a connecting shaft C of the door D and a fixed fulcrum Sw fixed to the door frame W are connected by a link A. J rotates in the direction of arrow A in the figure, and the door D rotates in the direction of arrow B in the figure around the door pivot O. In the case of FIG. 9B as well, in the same manner as in FIGS. 9A and 9C, the “distance between the connecting shaft C and the fixed fulcrum Sw” is minimized so that the door faces the straight line Ts. Rotate. When the position of the connecting shaft C is on the straight line Ts, the door stops.
When the door passes the position of Ts and continues to rotate in the direction of arrow B in the figure and reaches D5, the “distance between the connecting shaft C and the fixed fulcrum Sw” increases, and the rotating body J is in the direction opposite to the arrow a in the figure. Rotate to.

FIG. 9D shows a connecting shaft C of the door D and a connecting shaft P provided at the tip of the rotating body J that rotates around the fixed fulcrum Sw. The door D rotates in the direction and closes and rotates in the direction indicated by the arrow B in the figure around the pivot axis O of the door. FIG. 9D operates so as to minimize the “distance between the door pivot O and the fixed fulcrum Sw”, and the door pivot O, the connection axis C, and the connection axis P are aligned in a straight line. Is stationary. When the connecting shaft P is on T5, T30, Ts, the door is stationary.
9 (b) and 9 (d), the traction point in FIG. 1 is the connection axis P, the towed point in FIG. 1 is the fixed fulcrum Sw in FIG. 9 (b), and the connection axis in FIG. 9 (d). C. The straight line connecting the traction point and the towed point is an action line of force acting on the door, and when the force action line passes through the pivot axis O of the door, the rotation of the door stops.

In the apparatus described with reference to FIGS. 9B and 9D, the door is stationary immediately before closing, and neither the rotating body J nor the door D can continue to rotate. FIGS. 10 to 13 are devices having the same structure as FIGS. 9A and 9C, and the door can continue to rotate even when the door is stationary.

In the embodiment shown in FIGS. 10 and 11, the link A is connected to the fixed fulcrum Sw fixed to the door frame W and the “connection shaft P provided at the tip of the rotating body J that rotates about the connection shaft C of the door D”. Then, the rotating body J rotates in the direction of the arrow A in the figure, and the door D rotates in the direction of the arrow B in the figure around the door pivot O. The structure of the embodiment shown in FIG. 10 is a structure in which the link A and the rotating body J overlap each other when the door is at a stationary position so that the rotating body J and the door can continue to rotate. The structure of the embodiment shown in FIG. 11 allows the wheel B, which is the rotation axis of the link A, to move along the sliding surface KK when the door is at a stationary position, so that the rotating body J and the door continue to rotate. This is a structure that can be used. The structure of the embodiment shown in FIG. 12 is such that when the door is at a stationary position, the wheel BB, which is a connecting shaft between the link A and the rotating body J, can move in the elongated hole Hj. The structure allows the rotation to continue.
The structure of the embodiment shown in FIG. 13 is a structure in which the link A of FIG. 9 is made into two links A and AA, and when the door is at a position where the door is stationary, the link A and the rotating body J are integrated. In this structure, the rotating body J and the door can continue to rotate.

In FIG. 11, the sliding surface KK along which the wheel B moves includes a recess KK1 and a linear portion KK2. At the position of D10 where the sealing operation starts, the axis core line of the rotating body J and the straight line portion KK2 are orthogonal to each other. The wheel B starts to slide on the straight portion KK2 and moves on the sliding surface K1 away from the recess KK1.
When the door of FIG. 11 is opened from the closed state, the wheel B moves along the sliding surface K2. However, when the door is opened, the sliding surface K2 moves in a direction opposite to the direction pushing the wheel B. The door and the relative movement are relatively large. The sealed state is easily released and the door is easy to open. Compared to this, when opening the door of FIG. 10 from the closed state, the wheel B moves along the sliding surface K2, but the moving direction of the wheel and the opening direction of the door are the same direction, and the wheel B and the door There is relatively little movement. The sealed state is difficult to release and the door is difficult to open.

In FIG. 12, the wheel BB moves along the sliding surface K on the inner side surface close to the door D of the long hole Hj provided in the rotating body J, and the sliding surface K includes the start end K1, the straight line K2, and the end K3. The wheel BB stays at the start end K1 in the “rotation range before the start of the sealing operation (A)”, and the axis A of the link A and the straight line portion K2 are orthogonal to each other at the position D10 where the sealing operation starts. When the position of D10 is passed, the crossing angle between the axis A of the link A and the straight line portion K2 exceeds 90 degrees, and the wheel BB starts to slide on the straight line portion K2 in the direction of the arrow C in the figure, away from the concave portion K1, and the terminal portion. Move to K3. At this time, even if the door D is stationary, the rotating body J rotates and the wheel B is located far from the door pivot O and rides on the sliding surface K attached to the door D to seal the door.

10 and 11, the action point of the force for pulling the door in the “rotation range before the start of the sealing operation (A)” is in the vicinity of the door pivot axis O, and “the action line Tf of the force Fb and the door pivot axis”. “Distance Lf” is reduced, the door is rotated by the reduced force moment M, and the wheel B slides far away from the door pivot O in the “rotation range (i) after the sealing operation starts”. By moving along the moving surface K, the “distance Lf between the action line Tf of the force Fb and the pivot axis O of the door” is increased, and the door is brought into close contact with the door stop by the increased moment M of the force. Yes. 10 and 11, the sliding surface K far from the pivot axis O of the door is separated into the sliding surface K1 and the sliding surface K2, and moves along the sliding surface K1 at the beginning of the sealing operation, and thereafter the sliding surface K1 slides. By moving along the moving surface K2, the “distance Lf between the action line Tf of the force Fb and the pivot O of the door” is increased only when the latch is recessed in the door.

FIG. 10 (c) is an elevational view showing a state in which the closing device is closed, and the rotating body J rotates around the connection axis CZ of the bearing Zc attached to the door D. The link AA and the wheel B operate above the upper end XX of the door D. The sliding surface K and the fixed fulcrum Sw are attached to the door frame W above the upper end XX of the door D.
FIG. 11C is an elevation view showing a state in which the closing device is closed. The sliding surface KK is attached to the plate Zd attached to the door D, and the sliding surface K is attached to the door frame W. The wheel B moves away from the sliding surface KK and comes into contact with the sliding surface K in the “rotation range (i) after the sealing operation starts”. The rotating body J, the link A, and the wheel B operate above the upper end XX of the door D. The sliding surface K and the fixed fulcrum Sw are attached to the door frame Wu above the upper end XX of the door D.

The operation of FIG. 13 and its technical features will be described.
FIG. 13 shows a link device of a connecting portion for connecting a connecting shaft P provided at the tip of the rotating body J and a connecting shaft C of the door by two links A and AA. The rotating body J is attached to the door frame. The door D rotates about the fixed fulcrum Sw in the direction of arrow A in the figure, and the door D rotates about the rotation axis O in the direction of arrow B in the figure. The two links A and AA are connected by a connecting shaft PP. The rotating body J is rotated by a spring (not shown).
In FIG. 13A, the state where the door D is fully opened is indicated by a solid line. The rotating body J, the link A, and the link AA are in a straight line, and the door D is fully open. The distance between the fixed fulcrum Sw and the connecting shaft C is the sum of the length of the rotating body J, the length of the link A, and the length of the link AA.
13A to 13B, the two links A and AA are kept in a straight line from the fully opened state to just before the door is closed, and the connecting shaft P rotates about the fixed fulcrum Sw to pull the connecting shaft C. At this time, the radius of rotation of the connecting shaft P is rp shown in FIG. 13B.
As shown in FIG. 13 (a), the rotating body J and the link A are bent from a straight line indicated by a solid line into a “shape” around the connection axis P as indicated by a dotted line, and shown in FIG. 13 (b). As shown in the figure, the link A hits the contact Gj provided by the rotating body J immediately before closing, and the rotating body J and the link A connected thereto contact each other on the side surface, so that the rotating body J and the link A are in close contact with each other. The connecting shaft PP rotates about the rotating shaft Q and pulls the connecting shaft C. At this time, the rotation radius of the connecting shaft PP is rpp shown in FIG. 13B.
Thus, the rotation radius of the traction point becomes extremely small, and the integrated link A and the rotating body J are “a lever with the rotation axis Q as a fulcrum, the connection shaft P as a force point, and the connection axis P as an action point”. Become. Due to the lever principle, the door is strongly pressed against the door stop Gd.

The traction point moves from the connecting shaft P to the connecting shaft PP, and the connecting shaft PP makes a circular motion around the fixed fulcrum Sw with a “radius rpp between the length of the rotating body J and the length of the link A” as a turning radius. At the moment when the link A hits Gj, the “distance between the fixed fulcrum Sw and the connecting shaft C” is “the difference rpp between the length of the rotating body J and the length of the link A”.
When the turning radius of the traction point suddenly changes to a small value, the moment acting around the fixed fulcrum Sw is suddenly converted into a large traction force so that it acts greatly when the latch is recessed inside the door. As described above, the means for switching from the range (A) to the range (I) is such that the link A and the rotating body J are integrated to reduce the rotation radius of the traction point, thereby reducing the magnitude of the force acting on the door. It is continuously increasing.

In the embodiment of FIG. 13, a large force suddenly acts at the end of the rotation of the door. Similar to the other embodiments of the present application, the common point is that the “distance between the line of action of force and the center of rotation” suddenly increases. As will be described later, the embodiment of FIG. 13 also has a function of decelerating when sealed. The speed reduction mechanism of FIG. 13 is the “means for controlling the direction of force without using resistance” as in the other embodiments of the present application, and is decelerated by “the movement speed becomes zero when the direction of movement is reversed”. ing. The deceleration means is a "means for converting the inertial force attached to the door into a braking force", and the device has a self-control function in which the braking force changes depending on the magnitude of the inertial force, and against a particularly large inertial force. A link device that stops rotating.

The line of action of the force pulling the door is the axis Aa of the link AA. FIG. 13 (a) is an operation explanatory diagram in the range (A) in which the fully opened state is indicated by a solid line, and the state before the closing dimension is indicated by a broken line, and FIG. It is explanatory drawing. The axial center line of the link AA shifts from a state parallel to the door surface to a right angle state in the “range from fully open to immediately before closing (A)” so that the traction force acts more strongly on the door.
In FIG. 13 (f), the fully opened state is indicated by a broken line, and the state just before closing is indicated by a solid line. Stop or slow down.
In the embodiment of FIG. 13 as well, as in the embodiment of FIGS. 1 to 12, the device continues to rotate even if the door stops immediately before closing. FIGS. 13 (c) to 13 (e) It is operation | movement explanatory drawing of the apparatus which transmits to a sealing device, without transmitting to rotation of a door.
The embodiment of FIG. 13 (f) differs from the embodiment of FIGS. 13 (a) to 13 (e) in that the structure and the door operation direction are different. The position of the pivot axis O of the door is different and the rotation direction of the door is reversed.

FIGS. 13C to 13E are technical explanatory diagrams for stopping the door when it suddenly accelerates and rotates due to a gust of wind and the like so as not to be sealed, and the operation from immediately before closing to closing is described. .
As shown in FIG. 13C, the connecting shaft PP10 revolves around the connecting shaft C and simultaneously revolves around the fixed support shaft Sw. The circular track C is a circle centered on the position C10 of the connecting shaft immediately before closing, and when the connecting shaft PP10 moves inside the circular track C, the door rotates in the opening direction, so that the connecting shaft PP10 moves to the circular track Ha. When moving outside the door, the door rotates in the closing direction. When moving inside the circular track C and rotating in the direction in which the door opens, the rotation of the door stops when a force in the direction of closing the door is applied due to a gust of wind or the like.
In any case, the movement of the connecting shaft PP10 moving in parallel with the closed door suppresses the movement of the door closed by inertial force.

When the door is closed and rotated, the area before the connecting shaft PP crosses the “straight line Tcs passing through the connecting axis C and the fixed fulcrum Sw” is referred to as “pre-crossing area”, and the area after crossing is referred to as “post-crossing area”. When the connecting shaft PP is in the “pre-cross-border region” and the rotating body J rotates in the direction of the arrow a in the figure, the door rotates in the closing direction, but the connecting shaft PP is in the “post-border region” in the figure. When rotating in the direction of arrow C, the “distance between the connecting shaft C and the fixed fulcrum Sw” increases and the door rotates in the opening direction.
“Before cross-border area” is an area (e) that does not include the pivot axis O of the door bounded by the straight line Tcs passing through the connecting axis C and the fixed support shaft Sw, and the “post-cross-border area” includes the pivot axis O of the door. An area.

Before the “link A hits Gj” shown in FIG. 13C, the connecting shaft C, the connecting shaft PP, and the connecting shaft P are in a straight line, and the connecting shaft P continues to pull the connecting shaft C of the door. In the case where the link A is bent into a “U” shape at the tip portion as in the thirteenth embodiment, the “straight line Tcp passing through the connecting shaft C and the connecting shaft P” is always the fixed supporting shaft when the rotating body J continues to rotate. Cross Sw. That is, the connecting axis PP crosses the “straight line passing through the connecting axis C and the fixed fulcrum Sw” and enters the “post-border boundary region”.
Even if the link A is a straight straight line and cannot be bent at the tip, the “straight line Tcp passing through the connecting shaft C and the connecting shaft P” is fixed to the fixed fulcrum Sw depending on the position where the contact Gj is attached. Can be crossed. In this case, the link A must pass over the fixed support shaft Sw.

When the inertia force attached to the door is large when the link A hits the contact Gj, the inertia force rotates the link AA in the direction opposite to the direction indicated by the arrow C in the figure, and rotates the rotating body J in the direction opposite to the direction indicated by the arrow A in the figure. The rotating body J rotates in the direction opposite to the spring biasing direction, and the closing device in FIG. That is, the inertia force changes to a braking force according to the magnitude.
Whether the inertia force is large or small, the door will eventually stop and disappear. When it disappears, the rotating body J rotates again in the direction of arrow A in the figure, and the link AA rotates in the direction of arrow C in the figure. The door rotates in the opening direction and then closes.

As shown in FIG. 13B, when the connecting shaft PP is in the “post-border area”, when the “door closing force” is applied to the door D, the rotating body J rotates in the direction to open the door, and “opens the door”. When "force" is applied, the rotating body J rotates in the direction to close the door. When the connecting shaft PP is in the “post-border zone”, the door cannot be rotated even if a force is applied to the door by applying a force from the outside. The door rotates only when the rotating body J rotates. This means that even if the door is pushed in the closing direction shown in FIG. 13 (b), the door does not move, and this is an effective means for preventing a finger jamming accident. However, if the door is closed, it will not open. It means that.
When the link A is bent into a “shape” at the tip, it always enters the “post-border area” when the door is closed. When the door is closed, the connecting shaft PP is in the “before-border zone”, but when the closed door is opened a little, it always enters the “after-border zone”. Therefore, it is impossible to open the closed door.
FIGS. 13C to 13E illustrate means for enabling a closed door to be opened when the link A is bent into a “U” shape at the tip, and the door is opened. It is explanatory drawing of the non-return valve which prevents that the connection axis | shaft PP may penetrate | invade into a "post-border area again". The wheel B is mounted on the rotating body J so that the door is opened, and the wheel B moves along the sliding surface K attached to the door frame W. When the door is closed, the sliding surface K moves the connecting shaft PP from the “before-border zone” to the “after-border zone”, but does not move from the “after-border zone” to the “before-border zone” when the door is opened. This is a check valve.
13C to 13E, the connecting shaft P moves in the direction opposite to the arrow D in the figure, and the wheel B moves along the sliding surface K in the direction away from the fixed support shaft Sw. The “straight line Tcp passing through the connecting shaft C and the connecting shaft P” traverses the fixed fulcrum Sw, and the connecting shaft PP opens again without returning to the “post-border boundary region”.

Examples of FIGS. 14 to 18 will be described.
14 to 18 show doors having a structure in which the connecting shaft C of the door D and the fixed support shaft Sw of the door frame W are connected to each other by a pulling spring V, and one end of the pulling spring V is attached to the door. A door that rotates with the other end far from the position close to the door pivot axis O and the spring shaft core line close to the door pivot axis O, and has a “rotating means in the range (A)”. The sealing device is mounted at a position far from the door pivot O, and has a "rotating means in the range of (ii)" in which the spring force acts at a position far from the door pivot O. FIGS. 14 and 15 show the rotating device when the connecting shaft C is close to the pivot O of the door as shown in FIG. 9C, and FIGS. 16 and 17 show the fixing as shown in FIG. 9A. A sealing device is added to the rotating device when the support shaft Sw is located near the pivot axis O of the door.

10 to 12, the connecting shaft C of the door D and the fixed support shaft Sw of the door frame W are connected by a “connecting body composed of the link A and the rotating body J”. The structure on the end side far from O operates with the opening of the predetermined door as a boundary, so that the sealing device is activated, and the sealing device continues to operate even if the door is temporarily stopped. FIGS. 14 to 17 show that “the end portion of the spring V far from the door pivot O” operates at a predetermined door opening, so that the sealing device is activated and the door is temporarily stopped. The sealing device keeps operating. In FIG. 18 as well, the sealing device operates at a predetermined door opening, and “rotating means in the range (A)” to “rotating means in the range (I)” as in the case of FIGS. “Switching means” for switching to

The structure of FIGS. 14 to 17 is the same in that the structure of FIGS. 3 and 4 is composed of a spring / link connection. The spring mechanism of FIGS. ) ”Rotating means”, “(ii) range rotating means” and “switching means” are the same.
The tension spring V connects the sealing device far away from the door pivot O and the vicinity of the door pivot O, and the rotation shown in FIG. It fulfills the function of the device and fulfills the function of the sealing device in the “range from just before closing to the time of closing”. In the operation of the “switching means”, the springs of FIGS. 14 to 17 rotate the rotating body J so that the springs of FIGS.

In FIGS. 3 and 4, the spring core crosses the rotation axis of the link A, so that the switching is made from “rotating means in the range (A)” to “rotating means in the range (I)” at the door opening. As shown in FIGS. 14 to 17, the axis of the spring crosses the rotation axis Q of the rotating body J so that the opening degree of the door is the boundary, and the rotation means in the range of (A) to the range of (I). "Rotating means".
14 and 15, the link-side end of the coupling body is attached to the door frame W, and the spring-side end of the coupling body is attached to the door D as shown in FIG. 3. In FIGS. 16 and 17, the link-side end of the coupling body is attached to the door D, and the spring-side end of the coupling body is attached to the door frame W as shown in FIG. 4.
2 to 4 have a structure including a “continuous body AV connecting the spring and the link A”, and FIGS. 14 to 17 also include a structure including a “continuous body JV connecting the spring and the rotating body J”. Have the same behavior. 2 to 4, the moving support shaft Sj is a middle connecting shaft of the continuum AV and circularly moves in a region closer to the pivot axis O of the door than the rotation shaft of the link. However, in FIGS. Circular motion in a region farther from the pivot axis O of the door than the rotational axis Q of the rotating body J.

14-17, the door D and the rotary body J rotate with one spring V, but in FIG. 18, the door D and the rotary body J operate with separate springs V1, V2. The spring V1 rotates the door D, and the spring V2 rotates the rotating body J. The spring V2 is a toggle spring that keeps the rotating body J at a position different from the “(A) range” in the “(A) range”.
In FIGS. 2 to 4 and FIGS. 14 to 17, the rotating operation of rotating the door is automatically switched from the rotating operation of rotating the door to the operation of sealing the door, but the spring axis is just before the door is closed. And a straight line Ts passing through the fixed support shaft Sw, and a stop state. To such a rotating device, a sealing device that starts rotating when the axis of the spring crosses the rotating shaft of the rotating body J is added.
14 to 17, if there is a force to rotate the rotating body J even if the spring force does not have the force to rotate the door at the end of “range (A)”, the “rotating means in range (I)”. In FIG. 18, the wheel B moves along the sliding surface K1 to rotate the rotating body J, and the axis of the toggle spring V2 crosses the rotating shaft Q of the rotating body J, thereby limiting the opening of the door. Then, the “rotating means in the range (A)” is switched to the “rotating means in the range (I)”. Since the rotating body J rotates with the force of rotating the door, the rotating body J cannot be rotated unless the force of the spring V1 has the force to rotate the door. However, FIG. 18 is also the same as FIGS. 14 to 17 in that it includes “rotating means in the range (A)”, “rotating means in the range (I)”, and “switching means”.

In FIG. 18, the hit Gj is a hit for preventing one of the rotating bodies J from rotating, and the other rotation of the rotating body J is stopped when the door D hits the door-stopping Gd and the rotation of the door is blocked. . In many of the operation explanatory diagrams related to the doors of the present application, the door stop Gd is omitted for the sake of simplicity.
In FIG. 18, the rotary body stops in the “range (A)” without rotating by the toggle spring V <b> 2 and the contact Gj, and in FIGS. 3, 4 and FIGS. In this range, the rotating body is stationary without rotating.
The structure shown in FIGS. 3 and 4 and FIGS. 14 to 17 is a door that is rotated by a single spring shown in FIG. 1, and a connecting member composed of the spring and the rotating body J connects the connecting shaft C and the fixed support shaft Sw. The rotating body J has a contact G for preventing one of the rotations of the rotating body J, and the rotating body J starts to rotate away from the contacting Gj when the axial center line of the spring crosses the rotating shaft of the rotating body J. After the rotating body J starts to rotate, the spring expands and contracts as the rotating body J rotates to weaken the spring force. However, the distance between the spring axis and the rotating shaft of the rotating body J increases, and the rotating body J rotates. The rotational force acting on the body J increases.
3, 4 and 18, the expansion and contraction of the spring according to the rotation of the rotating body J is reduced by bringing the “end of the spring not connected to the rotating body” closer to the center of rotation. In FIGS. 14 to 17, “the end of the spring that is not connected to the rotating body” is moved away from the center of rotation, so that the length of the spring is increased and the expansion / contraction rate of the spring according to the rotation of the rotating body J is increased. It is small.

14 to 17, as in FIGS. 3 and 4, the rotating body J rotates when the spring V crosses the rotation axis Q of the rotating body J. 3 and 4 change the direction of the working force as the rotating body J rotates. In FIGS. 14 to 17, the position of the force application point suddenly changes from a position close to the door pivot O to a position far from the door. To do. The more the sealing device is provided at a position far away from the pivot axis O of the door, the greater the magnitude of the sealing force.
14 to 17 are the same as FIGS. 3 and 4 in that the change in the force acting on the door is “a sudden increase at the end of the door rotation”.
As in FIGS. 3 and 4, the rotating body J in FIGS. 14 to 17 rotates automatically at the end of the rotation of the door. It does not cause a strong force to act. In FIG. 18, it is necessary to apply a special force to start the toggle spring.

14 to 17, unlike the embodiments of FIGS. 10 to 12, the connecting shaft C and the fixed support shaft Sw are connected not by a rigid link but by an elastic spring, and are connected by a rigid link. In this case, there is a one-to-one correspondence between the rotation angle of the door and the rotation angle of the rotator J. However, in the case of a spring, the rotator J is not necessarily rotated simply by expanding and contracting. Even if the axis line crosses the rotation axis of the rotating body, the rotating body may start to rotate with a delay.
In other words, there is a time lag between the position of the spring core and the rotation of the rotating body. When the rotational speed of the door is abruptly high, the rotating body does not rotate even if the spring core crosses the rotating shaft of the rotating body. In some cases, the door may rotate.
In this case, as shown in FIGS. 15B and 16B, the wheel B engages with the sliding surface K1 before contacting the sliding surface K2. In the case of FIG.15 (b), rotation is suppressed, rotating the rotary body J to the arrow A direction in the figure, when the wheel B presses the sliding face K1. In the case of FIG. 16B, the force Fb that the wheel B presses the sliding surface K1 passes through the side of the rotating shaft Q close to the pivot axis O of the door, thereby rotating the rotating body J in the direction opposite to the arrow A in the figure. The rotation is prevented by Gj. As a result, the door stops just before closing and does not seal.

In this case, the inertial force attached to the door suppresses or reversely rotates the sealing device and acts as a braking force, and the magnitude of the braking force is proportional to the inertial force attached to the door. When the inertial force disappears, the effect disappears and the sealing device returns to the state of rotating in the forward direction.
The means to stop the door just before closing and prevent it from being sealed is only to cause a collision between the door and the door stop before the door comes in contact with the door stop, and not to reduce the impact received by the door. Absent. However, this means does not function when the door rotates at a normal speed, and when the door is struck by a strong wind and the door has dynamic inertia, it stops in an open state just before sealing. This operation prevents a finger jamming accident.

FIG. 16B shows a state in which the wheel B is engaged with the sliding surface K1 when the rotating body J starts to rotate, but the wheel B slides when the door has no dynamic inertia. Without pressing the surface K1, the rotating body J rotates in the direction of arrow A in the figure. When the door has dynamic inertia, the rotating body J rotates in the direction opposite to the arrow A in the figure, and the door stops.
Such an operation becomes possible by rotating the rotating body J regardless of the rotation of the door. Even if the spring does not have the force to rotate the door at the end of "Rotating means in range (A)". The rotating body J can be rotated only by the axis of the spring crossing the rotation axis Q. Even if the spring does not have the force to rotate the door, the door is strongly pressed and sealed by switching to “rotating means in the range of (ii)”.

If the spring is a rigid body, the rotation of the door and the rotation of the rotating body J are linked, and if the door stops rotating, the rotation of the rotating body J also stops. 3 and 4 and FIGS. 14 to 17 use springs so that the sealing device operates independently of the rotation of the door. If the spring is rigid, the door will rotate when the sealing force grows. By using the spring, it will grow to a strong sealing force even when the door is stopped.
The embodiment of FIGS. 10 to 12 is a case where the spring is a rigid body, and the rotation transmission means to the door is disabled so that the door is not rotated when the rotating body J rotates.
In this way, even if the door stops, the device will not stop, but at the same time, even if the `` switching means '' functions and a strong sealing force is generated, it will cause a slight rotation of the door from just before closing to sealing. Rotating the door does not accelerate the door.

FIG. 15 is an operation explanatory view of the sealing device of FIG. 14A is a view of the sealing device, FIG. 14B is a plan view thereof, and FIG. 14C is an elevation view thereof.
14 and 15, the sliding surfaces K1 and K2 are attached to the door D, and the rotating body J rotates about the rotating body rotation axis Q fixed to the door frame W. A rotating shaft Ib of the wheel is provided at one end portion of the rotating body J, and the wheel B is mounted on the rotating shaft Ib of the wheel. A tension spring V is attached to a fulcrum Sj provided at the other end of the rotating body J, and another fulcrum C of the tension spring V is attached to a connection axis C provided on the door D near the pivot axis O of the door. .

In FIG. 15A, the pulling spring V is “distant from the door D from the rotating body rotation axis Q” in the “range from fully open to just before closing” (a) until the sliding surface K1 contacts the wheel B. In the “region”, the rotation of the rotating body J in the direction opposite to the direction of arrow A in the drawing is prevented by the hit Gj. One fulcrum Sj of the tension spring V is stationary, and the other fulcrum C revolves around the pivot axis O of the door while reducing the length of the tension spring V. The door rotates in the direction of arrow B in the figure.
As shown in FIG. 15B, even if the door D further rotates and the pulling spring V passes over the rotating body rotation axis Q and moves to the “region closer to the door D than the rotating body rotation axis Q”. The position of the connection shaft C is on the fully open side (a) from the “straight line Ts passing through the door pivot axis O and the rotating body rotation axis Q”, and the length of the tension spring V continues to decrease. The pulling spring V passes over the rotating body rotation axis Q and the rotating body J rotates in the direction of arrow A in the figure, but the door D continues to rotate without stopping.
As shown in FIG. 15C, when the tension spring V moves to “an area closer to the door D than the rotating body rotation axis Q”, the rotating body J rotates away from the contact Gj. The “mechanism in which the rotary body J hits and rotates away from Gj when the axial core of the pulling spring V crosses the rotary body rotation axis Q” is the same as the spring mechanism of FIGS.
When the rotating body J rotates away from the hit Gj, the wheel B rides on the sliding surface K2 and presses the door D.

“The direction of the force Fb in which the wheel B presses the door D” is a substantially tangential direction of the circular motion of the door and is substantially perpendicular to the door surface. The pull spring V not only rotates the door from full opening to closing, but finally closes the door strongly.
If the “direction of the force Fb that the wheel B presses the door D” is perpendicular to the door surface, and if the wheel B rotates past the position perpendicular to the door surface, the closed door cannot be opened. The direction of the force Fb is inclined with respect to the door D surface so that resistance is not applied when the closed door is opened. When the closed door D is opened, the sliding surface K2 is inclined at an inclination angle Θd with respect to the door D surface to the extent that resistance is not applied. The wheel B moves on the sliding surface K2 in the direction opposite to the arrow A in the figure, passes between the sliding surfaces K1 and K2, and hits Gj.

When the pulling spring V passes over the rotating body rotation axis Q or before that, the position of the connecting shaft C is on the "straight line Ts passing through the door pivot axis O and the rotating body rotation axis Q" If the door does not rotate due to force, the door will continue to rotate due to the inertial force attached to the door. Thereafter, the tension spring V passes over the rotating body rotation axis Q, and the rotation of the rotating body J starts regardless of the rotation of the door, rotates even when the door is stopped, and seals the door.
When the inertial force attached to the door is large and the rotation of the rotating body J is delayed with respect to the rotation of the door, the sliding surface K1 is provided at a position where the wheel B contacts when the door continues to close and rotate without rotating the rotating body J. Before the transfer onto the sliding surface K2, the abutment against the sliding surface K1 stops the rotation of the door. This is to prevent the door from rotating rapidly due to a strong wind and colliding with the door violently, and is a means for preventing a fingernail accident.
3 and 4, the opening angle of the door when the rotating body J hits and leaves Gj in the process of closing the door is “rotating body J away from the hit Gj” in the process of opening the door. The opening angle of the door is smaller than the door opening angle when it comes into contact with Gj again, and the range in which the door rotates only by the inertial force in the process of closing the door is slid with the rotating body J remaining away from Gj in the process of opening the door. Even if the hand moves away from the handle within the range, the door does not stop.

16 and 17, the rotating body J attached to the door D rotates and the wheel B moves on the sliding surface K fixed to the door frame W, but one fulcrum Sj of the tension spring V is the rotating body. It is attached to J and revolves around the pivot axis O of the door. The other fulcrum Sw is attached to the door frame W and is stationary. The door D rotates in the direction of arrow B in the figure.
In the case of FIGS. 16 and 17, the tension spring V is connected to the rotating body rotation axis Q in the same way as in FIGS. 14 and 15 so that the spring mechanism of FIGS. Rotation J rotates in the direction of arrow A in the figure, and the door B is sealed by a force Fb that presses the sliding surface K2. The embodiment of FIG. 17 differs from the embodiments of FIGS. 15 and 16 in that it has the effect of reducing the rotational speed of the door when the wheel B moves while keeping contact with the sliding surface K2, and the wheel B moves on the sliding surface K2. The distance traveled is long. The sliding surface K1 rotates the rotating body J so that the wheel B moves on the sliding surface K2, and prevents the rotating body J from being closed without rotating.

In the case of sealing the door in the range (i) from immediately before closing to closing, in the case of FIG. 16C, the wheel B pulls the sliding surface K2 and pulls the door frame W to the door. In the case of FIG. 17C, the wheel B pushes the sliding surface K2 apart to draw the door frame W toward the door.
When the rotating body J rotates and begins to move along the sliding surface K2, “the direction Fb of the force that the wheel B acts on the door frame W” is the substantially radial direction of the circular motion of the door, and then gradually. It shifts from the radial direction to the circumferential direction, and becomes the substantially circumferential direction of the circular motion of the door when sealed.
When the closed door D is opened, the rotating body rotation axis Q revolves around the door pivot O at the same time. The position of the rotation axis Q of the rotating body moves from the side closer to the door D in the case of FIG. 15 with the tension spring V as a boundary, and moves from the far side to the near side in the case of FIGS. In the figure, it rotates in the direction opposite to the arrow A and hits Gj.

FIG. 18 shows separate springs for rotating the door D and the rotating body J, and the pulling spring V1 rotates the door in the “range from fully open to just before closing (A)”. V2 rotates the rotating body J in the “range from right before closing to the time of closing (i)”. The rotating body J swings between a position where it abuts against Gj and waits and a position where it abuts against the sliding surface K2 and seals, and the toggle spring V2 is kept stationary at the two positions, It does not rotate with the rotation of the door as in the embodiments of FIGS.
As shown in FIGS. 18A and 18B, the tension spring V2 rotates the rotating body J and seals the door regardless of the tension spring V1. The rotating body J hits Gj in the “range from fully open to just before closing (A)” and remains stationary, and in the “range from just before closing to the closing time (yes)”, the rotating body J rotates while being in contact with the sliding surface K1, moves away from Gj, and the wheel B applies force to the sliding surface K2.
When the closed door is opened, the rotating body J rotates while contacting the sliding surface K2, and comes into contact with Gj. When the door is closed, the wheel B moves along the sliding surface K1 without contacting the sliding surface K2.

FIG. 18A shows a structure in which the toggle spring V2 is attached to the rotating body J shown in FIG. 15. The rotating body J is attached to the door frame W, and the end of the toggle spring V2 is also attached to the door frame W. The door starts to rotate in contact with the surface K1, contacts the sliding surface K2, and seals the door.
FIG. 18B shows a structure in which the toggle spring V2 is attached to the rotating body J shown in FIG. 16, and the rotating body J is attached to the door D. In the “range from fully open to just before closing (A)”, the rotating body J abuts against the contact Gj and maintains the stationary state by the pulling spring V2. When the rotating body J comes into contact with the sliding surface K1 immediately before sealing, the toggle spring V2 rotates the rotating body J, and the wheel B attached to the rotating body J moves along the sliding surface K2 to seal the door. .

In the embodiment of FIGS. 14 to 17, the spring for rotating the door is the same as the spring for sealing, and FIG. 18 prepares the force of the spring for sealing the door separately. Therefore, the sealing device of FIG. 18 can strongly seal the door. However, as the sealing device shown in FIGS. 14 to 17, the rotating body J rotates freely and the wheel B slides as the door rotates. The rotating body J does not rotate even if it does not collide with K1, but the rotating body J rotates when the wheel B collides with the sliding surface K1, and in the case of FIG. The tension spring V1 has to rotate the door immediately before sealing and to rotate the rotating body J. Therefore, as in the case of FIGS. 14 to 17, the door cannot be decelerated due to insufficient spring force just before sealing, and it is necessary to increase the force of the spring as compared with the case of the sealing device shown in FIGS. As a result, the closing speed of the door immediately before sealing is increased.
As described above, FIG. 18 is different from FIGS. 14 to 17, but an operation is newly added from “(a) range of rotation means” to “(ii) range of rotation means” in the door closing rotation. It is the same in that it switches without permission.

In FIG. 18, as shown in FIGS. 14 to 17, even if the door does not rotate immediately before the sealing, the rotating body J does not reach the sealing by the rotation, but the rotating body J rotates by the rotational force of the door. In addition, the rotating body J rotates immediately before sealing, and at the same time, the wheel B moves along the sliding surface K1 or K2 and seals while rotating the door.
In the case of FIG. 18, it is necessary to continue the rotation of the door without losing the force in the middle. However, when the toggle spring is rotated by the rotation of the door, work other than the work of rotating the door is performed. The speed slows down.
When the rotating device and the sealing device are prepared separately as described above, when the operation is inherited from the rotating device to the sealing device, the energy of the spring is lost to activate the sealing device, so that the door is decelerated. Similarly, in the embodiment of FIG. 27 described later, when the operation is inherited from the rotating device to the sealing device, the energy of the spring is lost and the door is decelerated.

The wheel B and the sliding surface K2 are separated in a “range from fully open to just before closing (A)” and united in “range from just before closing to the closing (yes)”. In the case of FIGS. 14 to 17, the position through which the rotating body J starts to rotate when the door is closed is not relatively determined by the opening angle of the door, so the path through which the wheel B passes is not limited. Which position on which sliding surface the wheel B is on is relatively not limited by the opening angle of the door.
In the case of FIG. 18, when the closed door is opened, the wheel B moves along the sliding surface K2, and moves away from the sliding surface K2 after passing through the passage between the sliding surfaces K1 and K2. After the sliding surface K1 passes the side of the wheel B, the rotating body rotates and comes into contact with Gj. The wheel B stops at a position that does not contact the sliding surface K2 and a position that contacts the sliding surface K1, and when the door closes, the wheel B contacts the sliding surface K1 before contacting the sliding surface K2. The rotating body J rotates. The wheel B moves while pressing on the sliding surface K2, reaches the end of the sliding surface K2, and seals the door.

In the case of FIG. 18, it is difficult to consider the case where the rotating body J rotates before the wheel B contacts the sliding surface K1 when the door is closed as in the case of FIGS. When the rotating body J rotates before contacting the wheel, the wheel B is brought into contact with the sliding surface K3. At this time, the door is stopped, but it can be sealed by pushing with a hand. When the closed door is opened, if the rotating body J rotates before the wheel B contacts the sliding surface K1, the sliding surface K1 of the wheel B is in contact with the sliding surface K4. Pass by the side.
Since the device that applies a sealing force to the position away from the pivot axis O of the door has a large revolution radius of the wheel B, providing a passage that suppresses the trajectory of the wheel B enlarges the device and does not provide a passage. There is a problem that makes operation unstable. 46 and 49 will be described later with reference to FIGS. 46 and 49. These open and close the end wheel B and the sliding surface K2 are kept in contact with each other and the sliding surface K2 is not fixed by rotating. Device.

The embodiment of the door shown in FIG. 19 has a function of “rotating the door by a force acting near the pivot axis O of the door” in the range from fully open to immediately before closing, and “door door” in the range from immediately before closing to sealing. `` A function that presses the door against the door by applying a force far away from the pivot axis '' and rotates the door while decelerating, and immediately before closing, from `` work to rotate the door '' to `` door to door An opening / closing device that seals the door, and is used when the door is pressed rapidly.When an external force such as strong wind acts on the door and the door rotates rapidly, the door just before closing is temporarily stopped. Function ".

The sealing device shown in FIG. 19 operates only during a slight rotation of the door in the “range from just before closing to the closing time”, and operates in a small space near the door frame. Moreover, since it is attached at a position away from the pivot axis of the door, the door can be tightly sealed with a small spring force.
The rotating device shown in FIG. 19 rotates the door greatly in the “range from the fully open door to the closed door”, and by rotating the door at a low speed even with a large spring force by setting the action point near the pivot axis O of the door. It is possible to make it. Moreover, since the circular motion of the action point around the pivot axis of the door is small, the apparatus can be made small.

FIG. 19 is a plan view for explaining the operation. FIG. 19A shows the state of the door when fully opened, FIGS. 19B and 19C show the state of the door immediately before closing, and FIG.
A bearing Sz having a through hole Sh through which the shaft Sf penetrates is attached to the upper portion of the door surface, and the shaft Sf can reciprocate through the through hole Sh without rotating in the axis Z direction parallel to the door surface. Is attached to the door D via the bearing Sz. Wheels Bf and Bb are attached to both ends of the shaft Sf, and a push spring U is attached between the bearing Sz and the shaft Sf. The shaft Sf moves along the axis Z of the through-hole Sh in the direction of the arrow A in the figure, the wheel Bf presses the contact Wf fixed to the upper door frame, and the door D is centered on the door pivot O. Rotate in the direction of arrow B in the figure.
FIG. 19 (e) is a view of the door immediately before closing, and FIGS. 19 (f) and 19 (g) are elevation views showing the arrangement of the door components. W denotes a door frame, which employs a spline shaft as the shaft Sf and a spline boss as the bearing Sz. The wheel Bb is above the lower surface XX of the door frame, FIG. 19F shows the case where the wheel Bf is below the lower surface XX of the door frame, and FIG. This is the case.

The operation of the embodiment of FIG. 19 will be described.
When the shaft Sf moves along the axis Z of the through hole Sh in the direction of the arrow B in the figure, the movement of the wheel Bf is called forward, and the direction perpendicular to the closed door surface is the Y axis, and the closed door surface The parallel direction is taken as the X axis. As shown in FIG. 19 (a), the wheel Bf advances in the Y-axis direction in the range (a) from the time of full opening until just before closing shown in (b). The forward movement of the wheel Bf is suppressed by the contact Wf, and the “force for rotating the door” acts in the vicinity of the pivot axis O of the door, so that the wheel Bf acts weakly on the door even if the spring force is large. The action line Ff of “the force that rotates the door” is on a straight line passing through “the contact point bf between the wheel Bf and the contact Wf” and the rotation axis Ibf of the wheel, and “the action line of the force that rotates the door” and the door The distance Lf from the pivot axis O is small.
Even when the spring force reaches the maximum value when the door shown in FIG. 19A is fully opened, the door is in a state where the force is insufficient to rotate the door, and the door barely starts rotating without stopping. In the range (a) from the time of full opening to just before closing, the moving direction of the wheel Bf changes from the negative direction of the Y axis to the negative direction of the X axis, and the wheel Bf gradually moves forward and the door rotates greatly.

In the range (A) from just before closing shown in FIGS. 19B and 19C to the closing time shown in FIG. Is small. The “door rotating force Ff” acting in the vicinity of the door pivot is invalid, and instead, the wheel Bb is located far from the door pivot O along the “sliding surface K fixed to the door frame”. It moves and “the force Fb for rotating the door” works effectively.
When the wheel Bb moves along the sliding surface in the recess Kh at the time of closing shown in FIG. 19 (d), the action point of the force Fb is far away from the pivot axis O of the door. The distance Lb between the "force" action line Fb (the straight line passing through the wheel rotation axis Ibb and the contact point bb) and the door pivot O is large, and even if the spring force becomes small and the door reaches the door Press strongly.
When the “distance Lz between the axis Z of the through hole Sh and the door surface” is larger than the thickness Lw of the hit Wf, the wheel Bf passes over the hit Wf. As shown in FIG. 19 (d), when the point of action of the force Ff moves farther in the negative direction from the pivot axis O of the door, the force Ff may effectively work to rotate the door and seal the door. .

In the embodiment shown in FIG. 19, the “function to rotate the door” disappears immediately before closing and the “function to seal the door” starts to function, but the “function to rotate the door” immediately before closing does not disappear. Even if the door continues to rotate, since the wheels Bf and Bb are integrated with the shaft Sf, the “function to rotate the door” and the “function to seal the door” operate in conjunction, and the wheel Bb slides. When moving on the moving surface K, the forward movement of the wheel Bf is obstructed, the “function of rotating the door” is weakened, and the door closing speed is reduced.

In the range (a) from the fully open position shown in FIG. 19 (a) to just before closing shown in FIG. 19 (b), “the force for rotating the door” is the minimum force necessary to start the door barely rotating without stopping. Yes, in the state immediately before closing shown in FIG. 19 (b), the force to dent the latch inside the door is insufficient, but when the wheel Bb moves into the depression Kh as shown in FIG. The spring force weakened by the so-called wedge effect is decomposed into a strong force substantially perpendicular to the moving direction of the wheel Bb. The force that the wheel Bb moves parallel to the door surface is supported by the force Fb that the wheel Bb presses the sliding surface K and the force that strongly presses the door against the door, and “the force that rotates the door” The distance Lb between the line of action Fb and the pivot axis O of the door increases, and the door is strongly pressed against the door.
If a large force is applied to the door immediately before closing, the closing speed is accelerated. However, the greater the resistance when the latch is recessed inside the door, the further the door closing speed is not accelerated.

As shown in FIG. 19 (b), when the forward movement of the wheel Bb is blocked and the forward movement shown in FIG. If the width of the entrance of the recess Kh into which the wheel Bb is fitted is slightly larger than the wheel diameter of the wheel Bb, and the wheel Bb is barely fitted into the door, When an external force such as strong wind acts on the door and the door rotates and closes rapidly, the wheel Bb is transferred directly from the sliding surface K to the sliding surface KK without being fitted into the recess Kh. When Bb moves along the sliding surface KK, the ascending gradient is climbed, and the push spring U is contracted.
When the inertial force is released after the door is temporarily stopped, the force of the push spring U becomes “a force to rotate the door in the opening direction” when the shrunk push spring U is extended and returned, and immediately before closing. Stop the door.

When the door is closed, “the wheel Bb moves on the sliding surface K” gives resistance to the rotation of the door due to the rolling friction of the wheel to produce a deceleration effect. However, when the closed door is opened, the “wheel Bb slides. “Moving on the moving surface K” means that the push spring U is contracted, and the wheel Bb moves circularly around the pivot axis O of the door, so that the force acting on the wheel Bb is centered on the pivot axis O of the door. The wheel Bb is moved in the tangential direction of the circle to be perpendicular to this, and resistance is applied to the rotation of the door. The force Fb that seals the door at the time of closing becomes stronger at a right angle with respect to the door surface as the inclination of the sliding surface shown in FIG. 19D is parallel to the closed door. Resistance increases.
When the door is closed, resistance is applied to the rotation of the door in the same way as when the resistance is applied to the rotation of the door to produce a deceleration effect.

When the door is sealed, the acceleration of the door is less when the rotation of the door is as small as possible. However, when the closed door is opened, if the wheel Bb is moved in a direction perpendicular to the door surface by a small rotation of the door when the door is sealed, the wheel Bb does not escape from the depression Kh. In the case of FIG. 19, since the shaft Sf moves only in parallel with the door surface, it is difficult to open the door in the same manner as Kanuki. In the case of FIG. 19, the wheel Sb moves along a sliding surface with a gentle gradient, so that the shaft Sf moves in parallel with the door surface. Even in a normal door latch, a sliding surface having a slope is provided at the tip of the latch so as to move parallel to the door surface.
49 and 50, the wheel B moves in parallel with the door surface so that the sliding surface rotates. When the sliding surface is rotated, the rotation of the door accompanying the movement of the wheel B increases, and the resistance decreases when the door is opened.
41 and 42, the latch is rotated so that the latch is accommodated in the door.

FIG. 20 is provided with wheels BB and B at both ends of the link A so that the wheels Bf and Bb are provided at both ends of the shaft Sf in FIG. The door is closed by the wheel B away from the vicinity of the pivot axis O of the door, and the resistance when the closed door is opened by the circular movement of the wheel B is not moved parallel to the door surface. It is to make it smaller.
FIG. 20 shows a sliding surface provided in the vicinity of the pivot axis O of the door D of the door D. It is operation | movement explanatory plan view of the apparatus which pulls Kd and rotates the door D to the arrow B direction in a figure. A spring for rotating the rotating body J is not shown.

In FIG. 20, the moving body is a rotating body (D) that is rotatably supported around a rotating shaft (O), and the link is formed by using the rotating body (D) and the fixed portion (W) as a link. A link device that connects the rotating body (D) and the fixed portion (W) with one or more links (J, A,), and is adjacent to any one of the link devices. The slider (BB) is mounted on one of the two links (A, D) that match, and the other side is provided with a sliding surface (K) that moves along the slider (BB). The switchgear according to any one of claims 1 to 3, wherein the slider (BB) swings between a small position and a large position.
The angle of intersection between the sliding surface K and the axis of the link A is changed by the rotation of the driven shaft, and at the predetermined opening degree of the driven rotating body, “the action of the force acting around the driven shaft” A switchgear characterized in that the "distance between the line and the driven shaft" is constrained to be small or increased by releasing the restraint.

FIG. 20A shows a state in which the wheel BB moves along the sliding surface Kd but remains in the vicinity of the pivot axis O of the door and rotates the door D in the direction of the arrow B until just before closing. An attempt is made to contact the sliding surface Kdd farther away from the pivot axis O. The wheel BB rotates the door largely without moving much, so the door rotates slowly, and the pulling shaft P at the tip of the rotating body J pulls the sliding surface Kd via the link A immediately before closing. Goes to the door pivot O and the door D is in a paused state.
Even if the door D is in a temporarily stopped state immediately before closing, the rotating body J continues to rotate. In FIG. 20 (b), the wheel BB moves away from the sliding surface Kd, so that the function involved in the rotation of the door disappears. Moves greatly and contacts the sliding surface Kdd to seal the door. FIG.20 (c) shows the state of the door at the time of sealing.

The embodiment of FIGS. 21 and 22 is provided with two wheels Bf and Bb as in the embodiment of FIGS. 19 and 20, and the wheel Bf is held in the vicinity of the pivot axis O of the door to rotate the door. 6 is a structure in which the door is sealed with the wheel Bb away from the vicinity, and the sealing function of the embodiment of FIG. 6 is changed and replaced with a sealing device that operates at a position far from the pivot axis O of the door. FIG. 21 is a plan view for explaining the operation. FIG. 21 (a) shows the state of the door when fully opened, FIG. 21 (b) shows the state of the door immediately before closing, and FIG. FIG. 22A is a view showing a state immediately before the door of FIG. 21 is closed. FIG. 22 (b) is an elevational view of the door showing a state of sealing.
The wheel Bf that operates in the region close to the pivot axis O of the door is engaged in the rotation of the door in the range from (a) to when the door is fully opened until it is closed. The function disappears and the function of sealing the door occurs. The wheel Bb that operates by acting at a position far from the pivot axis O of the door in the range of (a) from just before closing to the time of sealing closes the door. The force with which the wheel Bf presses the sliding surface Kf suddenly changes the direction of the action line at the moment when the latch is recessed inside the door, increasing the “distance Lf between the force action line and the door pivot O”. ing.

The structure and operation of the embodiment shown in FIGS.
A rotating body J is rotatably supported around a rotating support shaft C provided on the door D, and the rotating body J is mounted with a wheel Bf on a rotating support shaft Ibf at one end with the rotating support shaft C in the middle. Then, the link A is connected to the rotation support shaft Ia at the other tip portion, and the wheel Bb is mounted on the rotation support shaft Ibb at the tip portion of the link A.
The sliding surface Wf near the pivot axis O of the door on which the wheel Bf moves in the range from “full open to just before closing (A)” and the “range from just before closing to the closing (yes)” range The sliding surface Wb far from the pivot axis O of the door on which the wheel Bb moves is fixed to the door frame.

The rotating body J rotates in the direction indicated by the arrow A in the drawing by a spring (not shown) that is weak when the door is rotated and acts strongly when the door is sealed, and the door B is pressed by the wheel Bf pressing the vicinity of the pivot axis O of the sliding surface Kf. It rotates in the direction of arrow B around the pivot axis O.
In the range from (a) to when the door is fully open to immediately before closing, the wheel Bf is in the vicinity of the door pivot O, the rotation of the rotating body J and the movement of the wheel are small, and the rotation of the door is large, that is, not shown. Since the expansion and contraction of the spring is small and the door is rotated greatly, even if the force of the spring is large, it is almost in a state of insufficient force to rotate the door. When the side on which the wheel Bf of the rotating body J is attached is a long branch, not only the rotating support shaft C is greatly separated from the pivot axis O of the door, but also the rotational force of the rotating body J is transmitted to the door more weakly. In other words, by converting the spring force into a “door rotating force” smaller, the sealing force with respect to the “door rotating force” is increased in a range from the fully open position to just before closing. I can do it.
The sealing force is set first at the time of design, but even if the required sealing force is large, the “force to rotate the door in the range from fully open to just before closing” can be reduced.

In the range from (i) immediately before the door is closed to (i) at the time of closing, the wheel Bf rolls along the sliding surface Kf in the direction indicated by the arrow C in the figure, and the wheel Bf moves away from the sliding surface Kf. The wheel Bb rotates greatly and acts on the sliding surface Kb far away from the pivot axis O of the door.
When the wheel Bf does not move away from the sliding surface Kf, the sealing mechanism is the same as in the embodiment of FIG. As shown in FIGS. 21B and 21C, the wheel Bf moves along the sliding surface Kf and suddenly moves away from the pivot axis O of the door. As shown in FIG. 21 (c), the distance Lf between the line of action of “the force Ff that the wheel Bf presses the sliding surface Kf” and the pivot O of the door increases, and the rotation of the rotating body J and the movement of the wheel The door rotation is small. That is, the expansion and contraction of the spring (not shown) is large, and the door is rotated small, so that the force for sealing the door is large even if the spring force is small.

When the wheel Bf moves away from the sliding surface Kf, the wheel Bf does not participate in the rotation of the door, and the wheel Bb moves along the sliding surface Kb. As shown in FIG. 21A, the sliding surface Kb is composed of a straight portion Wb and an end portion Wbh. Before the sealing, when the wheel Bb moves along the straight portion Wb, “the line of action of the force Fb and the pivot of the door” The distance Lb from O is small, and when the wheel Bb moves along the end portion Wbh during sealing, the direction of the line of action of the force Fb suddenly becomes a direction perpendicular to the closed door. The distance Lb "with respect to the pivot axis O increases.

The sealing device of FIGS. 21 and 22 will be described.
A weak tension spring Va is attached around the rotation support shaft Ia, and the wheel Bd is lightly pressed against the sliding surface Kd by the weak action of the tension spring Va and moves along the sliding surface Kd.
As shown in FIG. 22, the wheel Bb is attached to the upper end of the rotation support shaft Ibb of the link A, and the wheel Bd is attached to the lower end. The wheel Bb moves along the sliding surface Kb fixed to the door frame, and the wheel Bd moves along the sliding surface Kd fixed to the door in the direction of arrow D in the figure.
When the wheel Bb and the wheel Bd are fixed to the rotation spindle Ibb, the wheel Bb and the wheel Bd rotate in the direction indicated by the arrow E in the figure, and the wheel Bb travels while rotating in the reverse direction along the sliding surface Kb. Become a brake to slow down the door closing speed.

As shown in FIG. 21 (c), when the door is sealed, the rotation support shaft Ia rotates around the rotation support shaft C in the direction of arrow A in the drawing as the rotating body J rotates, and the rotation support shafts C, Ia , Ibb move so as to be aligned in a straight line and increase the distance between the rotation support shaft C and Ibb, so that the wheel Bb fits into the recess Wbh.
The wheel Bb receives “a small force parallel to the closed door” via the link A and is inserted between the sliding surfaces Kd and Kb2 to generate “a large force perpendicular to the closed door”. The door is strongly sealed by the so-called wedge effect.

The deceleration of the sealing device of FIGS. 21 and 22 will be described.
As shown in FIGS. 21 and 22, the sliding surface Kdd is attached to the door D, and the wheel Bd shown in FIG. 22 is moved along the passage Wk between the sliding surface Kdd and the sliding surface Kd. . The width of the passage Wk is slightly wider than the wheel diameter of the wheel Bd so that the wheel Bd can barely move along the passage Wk.
The wheel Bd presses the sliding surface Kd when sealing the door, but when moving along the passage Wk before sealing, the wheel Bd slides as shown in FIG. 22 (a) by the inertial force attached to the door. The wheel Bb is pressed by the moving surface Kdd and the wheel Bb is pressed by the sliding surface Wbb, and the wheels Bd and Bb are sandwiched between the sliding surface Kdd and the sliding surface Wbb, and the movement is suppressed. . Inertial force attached to the door is converted into braking force.

FIGS. 23 to 26 are explanatory views of the operation of the drive unit using the cam wheel rotary body rotation axis Qj as the drive shaft, and FIG. 27 is an explanatory view of the rotation mechanism of the drive unit using the cam body rotation axis Qk as the drive axis. The door rotated by the rotation mechanism of the drive unit drive unit is a door having the wheel rotation axis Qj or the cam rotation axis Qk as the door pivot O, or the wheel rotation axis Qj or the cam rotation axis Qk. This is a door that transmits the rotation of the drive shaft to the rotation of the pivot O of the door. The door shown in FIGS. 25 and 26 is a door in which the rotation of the drive shaft is transmitted to the door and the door rotates.
23 to 27, the cam body KK is rotatably supported around the cam body rotation axis Qk, and the cam wheel rotation body Jq is rotatably supported around the cam wheel rotation body rotation axis Qj. The cam wheel B is attached to a rotation support shaft Ib provided at the tip of the cam wheel rotating body Jq, and the cam wheel B moves along a cam body sliding surface K provided on the cam body KK.
The cam body sliding surface K in FIG. 23 is a straight line or a convex surface, and the cam body sliding surface K in FIG. 24 is a concave surface, and the cam wheel revolves around the drive shaft by the rotation of the cam body sliding surface K. In FIG. 27, the cam body sliding surface K revolves around the drive shaft by the rotation of the cam wheel.

FIG. 23A is an explanatory view of the operation, and FIG. 23A is an angle at which the door is fully opened when the link Ak rotates around the connection axis QQ and the cam body rotation axis Qk moves. Has increased.
In the process of closing the door from the fully open state, the link Ak first rotates around the connection axis QQ, and the cam body KK rotates around the cam body rotation axis Qk while the link Ak hits and contacts Gb.
FIGS. 23 (b) and 23 (c) show the state before the closing and the state when the cam body rotating shaft Qk does not move and the state when the cam body rotating shaft Qk moves, respectively.

During the entire process of closing the door, the cam body KK rotates in the direction of arrow A about the rotation axis Q, and the cam wheel rotates when the cam wheel rotation body Jq rotates in the direction of arrow C about the cam wheel rotation body rotation axis Qj. While moving along the sliding surface K, B moves on the circumference Rb centering on the rotating shaft Qj of the cam wheel rotating body in the direction of arrow B.
The sliding surface K of the cam body KK has a vortex K as the outer periphery, and a straight line connecting the contact point b between the cam wheel B and the sliding surface and the rotation axis Ib of the wheel B presses the cam wheel. As shown in FIG. 23 (a), the force acting line keeps a constant distance from the cam wheel rotor rotation axis Qj in the range from when the door starts to close until just before closing. In this range, the door rotates with a constant rotational force and the spring force is set to a weak force so that the door starts moving without stopping wherever the hand is released from the open door.

As shown in FIG. 23 (b), the cam body sliding surface is composed of a K portion engaged in a range (A) where the door rotates and a KB portion engaged in a range (I) where the door is sealed while decelerating, In the range (A), even if the cam wheel moves largely on the sliding surface K, the cam body rotation and the change in the length of the spring V are small. In the range (A), the cam wheel is on the sliding surface KB. Even if it is moved slightly, the rotation of the cam body and the change in the length of the spring V are large. Further, the distance between the action line Fb of the force with which the cam body sliding surface presses the cam wheel and the cam wheel rotating body rotation axis Qj is small in the range (A), and the rotational speed of the rotating body is low. ) Is large and the rotating speed of the rotating body is high.

The cam body KK is attached to the “metal fitting W attached to the door frame” via the link Ak, and the cam body rotation shaft Q revolves around the connection shaft QQ. The link Ak rotates around the connection axis QQ in the direction of the arrow D, and the adjustment screw GB attached to the metal fitting W adjusts the gap Lg between the metal fitting W and the link Ak to rotate the cam body and the cam wheel rotating body. The distance between the axis Qj can be adjusted, and the rotation speed of the door can be adjusted.

When the gap Lg between the metal fitting W and the link Ak is widened, the cam body rotating shaft Qk and the cam wheel rotating body rotating shaft Qj approach each other, and the action line Fb of the force that the cam body sliding surface presses the cam wheel and the cam wheel The distance between the rotating body rotation axis Qj is increased and the rotation speed of the cam wheel rotating body Jq is increased.
As shown in FIG. 23 (b), when the distance between the action line Fb of the force that presses the cam wheel and the cam wheel rotating body rotating shaft Qj is large, the cam body KK rotating shaft Qk does not move and the cam body moves. KK rotates around the rotation axis Qk in the direction of arrow A. During this time, the cam wheel B moves along the sliding surface K in the direction indicated by the arrow B on the circumference Rb with the cam wheel rotating body rotation axis Qj as the center. At the same time, the cam wheel rotating body Jq rotates in the direction of the arrow C around the cam wheel rotating body rotation axis Qj.

When the gap Lg between the metal fitting W and the link Ak is reduced, the distance between the cam body rotating shaft Qk and the cam wheel rotating body rotating shaft Qj is increased, and the cam body sliding surface acts as a force to press the cam wheel. The distance between the line Fb and the cam wheel rotator rotation axis Qj becomes smaller and the rotation speed of the rotator becomes slower.
As shown in FIG. 23C, when the distance between the action line Fb of the force pressing the cam wheel and the cam wheel rotating body rotation axis Qj is small, the link Ak rotates and the cam body rotation axis Qk moves. To do. After the link Ak hits and hits G2, the cam body KK rotates about the rotation axis Q in the direction of arrow A.
During this time, the cam wheel B moves in the reverse direction along the sliding surface K. At the same time, the cam wheel rotator Jq rotates in the direction of the arrow C about the cam wheel rotator rotation axis Qj. However, as shown in FIG. 23B, the cam body KK rotates without the cam body rotation axis Qk moving. The rotation of the cam wheel rotor Jq is slower.

FIG. 24 shows a cam body sliding surface having a function of closing and a cam body sliding surface having a function of tightly sealing after closing, and can be adjusted separately. Can be adjusted to the most desirable condition.
In FIG. 27, the “cam body sliding surface having a function of closing” and the “cam body sliding surface having a function of sealing tightly after closing” are rotated around different rotation axes to “close”. "Operation" and "Operation to close tightly after closing" are separated, and when the operation is inherited, it can be temporarily stopped and tightly sealed.

FIG. 24 is an operation explanatory view of an embodiment of “a closing device comprising a rotating body having two cam body sliding surfaces and two cam wheels of different shapes”, FIG. 24 (a) is a fully opened state of the door, FIG. FIG. 24 (b) shows a state immediately before closing, and FIG. 24 (c) shows a closed state. In the entire process of closing the door, the cam body KK rotates in the direction of arrow A about the cam body rotation axis Qk, and the cam wheel rotation body Jq rotates in the direction of arrow C about the cam wheel rotation body rotation axis Qj. At this time, the cam wheel moves in the direction of arrow B on the circumference Rb with the cam wheel rotating body rotation axis Qj as the center while moving along the sliding surface. When the cam body sliding surface presses the cam wheel, the cam wheel rotating body Jq rotates.

The cam body KK includes a cam body KK1 having a vortex K as an outer periphery and a cam body KK2 having a cam body sliding surface KA as an outer periphery. The cam body KK1 and the cam body KK2 are coupled by a connecting shaft Ik, The cam body KK2 can be rotated around the connection axis Ik to fix the angle between the cam body KK1 and the cam body KK2.
The sliding surface K of the cam body KK1 is a portion engaged in the range (A) where the door rotates, and the sliding surface KA is a portion engaged in the range (I) where the door is sealed while decelerating.

Cam wheels B1 and B2 are attached to two rotation support shafts Ib1 and Ib2 provided at the tip of the cam wheel rotating body Jq, respectively, and the preceding cam wheel B1 and the following cam wheel B2 are connected to the cam body sliding surface K It moves on KA and does not move on KA and K.
As shown in FIG. 24 (a), the preceding cam wheel B1 moves on the cam body sliding surface K in the range (A) in which the door rotates, and as shown in FIG. 24 (b), the preceding cam wheel. After B1 rotates the cam body KK, the preceding cam wheel B1 moves away from the cam body sliding surface K, and the subsequent cam wheel B2 comes into contact with the cam body sliding surface KA.

The distance between each of the rotation support shafts Ib1 and Ib2 provided at the tip of the cam wheel rotation body Jq and the cam wheel rotation body rotation axis Qj is different, and the rotation support shaft Ib2 of the subsequent cam wheel B2 and the cam wheel rotation body rotation shaft are different. The distance to Qj is larger than the distance between the rotation support shaft Ib1 of the preceding cam wheel B1 and the cam wheel rotating body rotation axis Qj, and even if the sliding surfaces KA and K moving along these have the same shape, “ When the “distance between the cam body rotation axis Qk and the cam wheel rotation body rotation axis Qj” is reduced, the rotation speed of the door decreases at a position far from the position where the door closes.

The shape of the cam body sliding surface KA shown in FIG. 24 (b) is such that the concave surface portion is centered on the cam wheel rotating body rotation axis Qj "from the contact point between the cam wheel B2 and the cam body sliding surface KA. In the case of a circle whose radius is “the distance to Qj”, “the line of action of the force by which the cam body sliding surface KA presses the cam wheel B2” faces the rotating body rotation axis O and does not resist the rotation of the rotating body.
Further, the convex surface portion of the cam body sliding surface KA near the cam body rotation axis Qk is a circle with a small radius, and the smaller the radius, the “line of action of the force that the cam body sliding surface KA presses the cam wheel B2”. The direction of the direction changes rapidly, and the distance between the line of action of the force and the cam wheel rotating body rotation axis Qj increases rapidly, and the door can be sealed with a large force.

The cam body KK1 and the cam body KK2 are connected by an adjustment bolt Bk, and the plates Gp1 and Gp2 that are attached to the cam body KK1 and the cam body KK2 have through holes with reverse screws, respectively, and the adjustment bolt Bk passes therethrough. is doing. When the adjustment bolt Bk is turned, the distance between the plates Gp1 and Gp changes, the cam body KK2 rotates around the rotation support shaft Ik, and the focal point of the concave surface portion of the cam body sliding surface KA moves, and the action of the force The direction of the line changes. In the case of FIG. 24, when the distance between the plates Gp1 and Gp is increased, the rotational speed of the rotating body is decelerated, and when the distance is decreased, it is accelerated.

In the case shown in FIG. 24B, the cam body sliding surface presses the cam wheel when the distance between the plates Gp1 and Gp is large and the angle Θ between the cam body KK1 and the cam body KK2 is large. The distance between the force action line Fb and the cam wheel rotating body rotation axis Qj is small, and the rotational speed of the door is reduced. As shown in FIG. 24 (c), when the cam wheel B2 passes through the convex surface portion of the cam body sliding surface KA close to the cam body rotation axis Qk, the distance between the force action line Fb and the cam wheel rotation body rotation axis Qj. Increases and tightly seals the door.

In FIG. 24, the closing speed of the door is adjusted by a spring. Within the range (A) in which the door rotates, the spring V has an action line of the force of the spring V, that is, the axial center line of the spring V has a small distance from the cam body rotation axis Qk to weaken the rotational force. While the spring V is away from the arcuate guide Ks, the axis of the linear portion of the spring V decreases with the cam body rotation axis Q as the door is opened, but when the door is fully opened, the linear portion of the spring V The spring V is in contact with the circular arc guide Ks so that the distance between the shaft core line and the cam body rotation axis Qk becomes zero and the moment around the cam body rotation axis Qk does not become zero.
Within the range (i) in which the door is sealed, the spring V moves away from the circular arc guide Ks, and the axial center line of the spring V gradually increases the distance from the cam body rotation axis Qk to increase the rotational force. The larger the distance between the fulcrum Sk of the spring V and the cam body rotation axis Qk, the farther from the arc guide Ks, the stronger the door is sealed.

FIGS. 25 and 26 illustrate a connecting portion that transmits the rotational force of the driving unit described in FIGS. 23 to 25 to the door D. The device is attached to the outer surface of the door that is opened by pulling the handle of the door. The drive unit is attached to the upper door frame, and is attached to a position higher than the door upper edge XX. The arm Da connected to the drive unit is at a position higher than the door upper edge XX, and the metal fitting Dw attached to the upper portion of the door is at a position lower than the door upper edge XX.
In FIG. 25 (a), the roller Db attached to the tip of the arm Da moves in the elongated hole Dh of the metal fitting Dw attached to the upper part of the door, and is at a position lower than the door upper edge XX. In FIG. 26B, the “arm Da and the link Dl connected to the metal fitting Dw attached to the upper portion of the door” are connected by the connecting shaft Dj. The connecting shaft Dj is at a position lower than the door upper edge XX.
All parts attached to the door and the door frame do not enter the area sandwiched between the door drive door and the door frame, and therefore do not block the door opening, which obstructs the person passing through the door opening. do not become.

In the embodiment shown in FIG. 25, the closing speed of the door can be adjusted by changing the distance between the cam wheel rotating body rotating shaft Qj and the cam wheel rotating support shaft Ib by the turnbuckle 10At.
In the embodiment shown in FIG. 25, the spring 28V2 for rotating the cam body rotation axis Qk extends and contracts along a circular arc guide Kss. As shown in FIG. 25 (a), the wheel 29B attached to the link 29S is separated from the sliding surface 29S, and the spring 28V2 and the link 29S that act only at the time of sealing are in a straight line.
FIG. 25 (b) illustrates the operation of the door D and the connecting portion rotating about the pivot axis O of the door. The roller Db attached to the tip of the arm Da moves in the elongated hole Dh of the metal fitting Dw attached to the upper portion of the door. The state of revolving around the cam wheel rotating body rotation axis Qj is shown.

In the embodiment of FIG. 26, the closing speed of the door is adjusted by the preceding wheel 26B2 rolling on the cam body sliding surface. When the door is closed, the spring 26V3 acts directly on the cam body 26KK1, and when the preceding wheel 26B2 leaves the sliding surface of the cam body and the following wheel 26B3 moves on the sliding surface of the cam body, suddenly the door A strong rotational force is applied to the door and the door is tightly sealed. In FIG. 26A, all of the link devices Da, De, Dw of the connecting portion are below the upper door frame lower end XX and operate on the same plane.
When a door closer is attached to an indoor door frame with insufficient strength, the burden on the door frame is reduced by transmitting the rotation from the vertical member of the door frame to the door. Moreover, the metal fitting attached to the door frame is L-shaped, and the reaction force of the rotational force is supported by both the vertical and horizontal members of the door frame.

FIG. 26B illustrates the operation of the connecting portion and the door D that rotates about the pivot axis O of the door. The rotation of the door is large with respect to the rotation of the arm Da, and the rotation of the arm Da occurs when the door is fully opened. It is difficult to reach the door, it is easy to rotate the door manually and it is easy to keep it stationary. Also, when the door is closed, the sealing force of the door is directed in the direction of the pivot axis O of the door, so that the door can be closed securely without damaging the door even if the door hinge is loosened and rattled. I can do it.

27A and 27B are operation explanatory views of the driving unit of the closing device that transmits the rotation about the cam body rotation axis Qk to the door. FIG. 27A is a fully open state of the door, and FIG. 27 (c) shows a state immediately before closing, and FIG. 27 (d) shows a state when sealed.
The cam wheel rotating body Jq attaches the cam wheel B1 to the tip, and rotates in the direction of the arrow D around the cam wheel rotating body rotation axis Qj. The cam wheel B1 is provided at the outer edge of the cam body KK1 and moves along the sliding surface K1, and the cam body KK1 rotates in the direction of the arrow C about the cam body rotation axis Qk. At this time, the cam wheel B3 moves on the circumference Rb centering on the cam body rotation axis Qk in the direction of arrow B.
The rotation of the cam body KK1 by the driving of the cam wheel rotating body Jq is a rotating means of “range from fully open to immediately before closing (A)”.

The rotating body KK2 is fixed to a drive shaft Q2 provided on the door frame W, and the cam body KK3 is rotatably supported at the intermediate portion via the cam body KK2 and the connecting shaft Q. The cam body KK3 is provided with a sliding surface KA on the side close to the rotation shaft Q2 and a sliding surface K on the side far from the rotation shaft Q2 with the connecting shaft Q in the middle. Is attached. The metal fitting W is provided with a sliding surface K3 and a contact Gw, and the contact Gw prevents the movement in one direction along the sliding surface K3 of the wheel B2. In the “range from fully open to just before closing (A)”, the cam body KK3 stands upright on the sliding surface K3 when it is in contact with the contact Gw and does not rotate around the connecting shaft Q and remains stationary. I keep it.
When the door is sealed, the cam wheel B3 comes into contact with the sliding surface KA of the cam body KK3, causing the cam body KK3 to be in the direction of arrow E about the rotation axis Q. At the same time, the rotating body KK2 rotates around the drive shaft Q2 in the direction of the arrow A in the figure by the bias of the spring V2, the cam wheel B3 moves along the sliding surface KA, and the cam body KK1 becomes the cam wheel rotating body rotating shaft. Rotate in the direction of arrow c around Qj. The rotation of the cam body KK1 by the driving of the rotary body KK2 is a rotation means in the “range from just before closing to the closing time (i)”.

The spring V1 is a spring that rotates the cam wheel rotating body Jq around the rotation axis Qj. One end of the cam wheel rotating body Jq is positioned far from the rotation axis Qj of the cam wheel rotating body Jq, and the other end of the door frame W Connect to a position close to the rotation axis Qj. The cam wheel rotator Jq is rotated by reducing the expansion and contraction of the spring, but the force of the spring V1 has no force to seal the door.
The force of the spring V1 is designed to have a force to rotate the cam body KK3 around the rotation axis Q by rotating the cam body KK1 without stopping before the rotation of the cam wheel rotation body Jq. When the cam body KK3 starts to rotate, the spring V1 loses the force to rotate the cam wheel rotating body Jq. However, once the cam body KK3 starts to rotate, the spring V1 does not rely on the force of the spring V1 and then is exclusively driven by the force of the spring V2. Rotate.
The device that applies rotation to the door and the device that seals the door each have a separate rotating shaft and rotate with the force of a separate spring. The force to seal the door and the force to rotate the previous door can be adjusted separately and each can be set to the most appropriate size.
That is, the rotation means in the range (A) and the rotation means in the range (A) can be set most appropriately. Also, when switching from the rotating means in the range (A) to the rotating means in the range (A), the rotating means in the range (A) works to start the rotating means in the range (A). Becomes a state close to deceleration or stop, and functions as a means for allowing time to elapse.
Also in FIG. 18, when the door is sealed, the spring V1 involved in the rotation of the previous door has a force to rotate the rotating body J stationary by the toggle spring V2, and performs the work of rotating the rotating body J in addition to the rotation of the door. By decelerating the door before sealing.

When the door is opened, the cam wheel B3 moves along the sliding surface K of the cam body KK3, so that the cam body KK3 rotates about the rotation axis Q in the direction opposite to the arrow E direction. The line connecting the rotation axis Q of the cam body KK3 and the rotation support shaft of the wheel B2 is orthogonal to the sliding surface K3. Even if the cam wheel B3 is separated from the sliding surface K of the cam body KK3, the cam body KK3 is Stand on K3.
The cam body KK3 self-supports on the sliding surface K3, thereby preventing the cam body KK2 from rotating in the reverse direction and securing the passage of the cam wheel B3 when it is closed.
The mechanism of the spring shown in FIG. 27 is “the sliding surface KA rotating around the drive shaft Q2, the wheel B3 revolving around the rotating shaft Qj of the cam wheel, and the spring rotating the sliding surface KA. , A releasable restraining means for preventing the rotation of the sliding surface KA, and a spring mechanism for revolving the wheel B by the rotation of the sliding surface KA, which seals the door when the closed door is opened. It is characterized in that the spring expands and contracts only occasionally and does not expand and contract in the “range from fully open to just before closing (A)”, and the wheel B2 mounted on the tip of the sliding surface KA is a sliding surface. The spring mechanism is provided with a releasable restraining means for preventing the rotation of the sliding surface KA by moving along K3, and rotating the sliding surface KA by standing upright on the sliding surface K3. It is.

A spring mechanism for rotating the drive unit will be described.
The embodiment shown in FIGS. 28 to 33 is a “spring mechanism that exerts a large force at the moment of rotating the door with a small force and sealing the door”, and “a spring with a small force that works only when the door is rotated”. And `` a spring with a large force that works only at the moment of sealing the door '', the former changes only when the door is rotated, and the latter changes only when the door is sealed To do.

The mechanism of the spring shown in FIG. 24 is “a drive shaft attached to the door frame, a guide that is fixed to the drive shaft and has a convex outer edge, and the distance between the outer edge and the drive shaft differs depending on the location, A rotation-side support shaft provided at the end, a fixed-side support shaft attached to the door frame, and a spring having the rotation-side support shaft and the fixed-side support shaft as fulcrums at both ends,
The distance between the drive shaft and the rotation side support shaft is sufficiently larger than the distance between the rotation shaft and the outer edge of the guide, and when the rotation side support shaft revolves around the drive shaft while stretching the spring, The shaft core of the spring gradually approaches from a position away from the guide, and the rotation side support shaft further rotates around the drive shaft so that the spring is stretched while being wound around the guide. A spring mechanism configured to generate a rotational force around an axis, wherein the spring axis line is greater than the rotational force around the drive shaft when the spring axis line contacts the guide. A spring mechanism that allows the rotational force around the drive shaft to increase when the guide rotates away from the guide.

The mechanism of the spring shown in FIG. 28 is “the drive shaft Q attached to the door frame, the rotating body J fixed to the driving shaft Q, and the rotation provided at the end of the rotating body J opposite to the driving shaft. The support shaft Sj2, the fixed support shaft Sw attached to the door frame and on the opposite side of the drive shaft Q, the link S2, the spring V2, and the link S2, which are connected by the connection shaft Sv2, come into contact with one side surface GS. As shown in FIGS. 28A to 28C, the link S2 is provided with the connecting shaft Sv2 at one end and the connecting shaft Sj2 at the opposite end, and the link S2 is connected. When the shaft is pivotally supported by the shaft Sj2, that is, the rotation support shaft Sj2, the distance between the link connection shaft Sj2 and the connection shaft Sv2 is the distance between the rotation support shaft Sj2 and the drive shaft Q. And attach the contact Gs to the rotating body J. Alternatively, as shown in FIG. 28 (d), when the connecting shaft on the opposite side of the connecting shaft S of the link S2 is rotatably supported by the fixed supporting shaft Sw, the connecting shaft between both ends of the link is between Is the distance between the fixed support shaft Sw and the rotating shaft Q, and when the rotating body J rotates with the hitting Gs attached to the door frame, until the rotating body J rotates halfway. The rotation of the rotating body J is stopped by stopping the rotation of the link S2 by the contact Gs, maintaining the contact state with the contact Gs, keeping the connecting shaft Sv2 at the position of the rotation shaft Q and preventing the spring V2 from expanding and contracting. The link G2 is separated from the link S2 in the middle, and the spring V2 is expanded and contracted so that the connecting shaft Sv2 is separated from the position Q of the rotating shaft, and acts on the rotating body J from the middle of the rotation. Spring mechanism ".

The mechanism of the spring illustrated in FIGS. 29 to 33 is “the wheel is attached to the link, and after the link moves away from the hit, the wheel moves along a sliding surface attached to the door frame, thereby The sliding surface is attached to the plate after the link is moved away from the contact so that the spring does not expand and contract by keeping the shaft in the position of the rotating shaft or the link is attached to the link. By moving along the wheel, the rotating shaft further rotates and the wheel attached to the link is attached to the door frame so that the spring is not expanded and contracted so that the connecting shaft is kept at the position of the rotating shaft. The spring is extended and retracted away from the sliding surface or the sliding surface attached to the link is separated from the wheel attached to the door frame so that the connecting shaft is separated from the position of the rotating shaft. And a mechanism of spring ", characterized in that acting in the middle of the rotation to the rotating member.

The mechanism of the spring shown in FIG. 27 is “the rotating body KK2 fixed to the driving shaft Q2 provided on the door frame and the arm KA rotatably supported around the supporting shaft Q provided on the rotating body KK2. A wheel B2 attached to the tip of the arm, a sliding surface provided on a door frame along which the wheel moves, and a spring V2 that rotates the rotating body KK2 around the drive shaft Q2. The wheel Ka2 is provided so that the arm Ka stands upright on a sliding surface provided on the door frame to prevent the rotation of the rotating body KK2 around the drive shaft Q2 so that the spring does not expand and contract. The arm KA, which has been upright by moving along the sliding surface provided on the door frame, rotates around the support shaft Q provided on the rotary body KK2, so that the rotary body KK2 becomes the drive shaft. The spring V2 rotates about Q2 A mechanism spring ", characterized in that acting on the rotary member KK2.

In FIG. 28, the rotation and sealing of the door are not processed by one spring but are processed by two springs. FIG. 29 shows a case in which a spring for sealing the door is suddenly generated with a large force only at the moment when the door is sealed, and the rotation of the door due to the suddenly generated large force is reduced.
FIG. 28 is an explanatory view of the mechanism of the spring described in FIG. 24. FIG. 28 is an operation explanatory view of a relay from the spring V1 engaged in the rotation of the door to the spring V2 engaged in the sealing. FIG. It is operation | movement explanatory drawing of the spring made to act.
In FIG. 28, the rotating body J fixed to the rotating shaft Q around the rotating shaft Q provided on the plate W rotates in the direction of arrow → i in the drawing to close the door.
Links S1 and S2 are rotatably supported on rotation support shafts SJ1 and SJ2 provided on the rotating body J, and tension springs V1 and V2 are connected to connection shafts SU1 and SU2 at the tips of the links S1 and S2, respectively. One end is connected. The other ends of the tension springs V1 and V2 are connected to a connecting shaft SA at the tip of the rotating arm A that is pivotally supported by the rotating shaft I attached to the plate W and a connecting shaft SW provided on the plate W, respectively.

28A shows a state when the door is fully opened, FIG. 28B shows a state immediately before closing, and FIG. 28C shows a state when the door is sealed. As shown in FIG. 28A, the link S1 rotates around the rotation axis Q while its side surface is connected to the rotation axis Q, and the end Sv of the link S1 moves circularly around the rotation axis Q. Thereafter, the link S1 is separated from the rotation axis Q, and as shown in FIG. 28B, immediately before the door is closed, the spring V returns to its natural length, and the spring force becomes zero.
In the process of shifting to FIGS. 28A to 28B, the length of the spring decreases to weaken the force, but the distance L1 between the line of action F1 of the spring force and the rotation axis Q increases, and the spring V1 is The rotational moment applied to the rotating body J is kept as constant as possible.
The spring V1 is a coil spring having a large coil diameter with respect to the length, and the position where the spring V1 returns to the natural length is constant. When the force of the spring V1 becomes zero, as shown in FIG. It rotates in the direction of arrow → b in the figure around the rotation axis I.

As shown in FIGS. 28 (a) and 28 (b), the link S2 is in contact with Gs from the time of full opening until just before closing, and keeps the end Sv2 at the position of the rotation axis Q. Accordingly, there is no change in the length of the spring V2 from the time of full opening until just before closing, and the force of the spring V2 is not involved in the rotation of the rotating body J.
As shown in FIG. 28 (c), before the spring fulcrum SV is separated from the rotation axis Q, the axis line of the link S and the axis line of the spring are bent, and the moment of separation becomes a straight line. Immediately before closing, the link S2 moves away from the contact Gs, and while increasing the distance L2 between the action line F2 of the force of the spring V2 and the rotation axis Q, the rotation moment around the rotation axis Q is increased and the door is moved with a strong force. Seal. At this time, the greater the distance between the rotating shaft Q and the connecting shaft SJ2, the greater the distance L2 between the action line F2 of the force of the spring V2 and the rotating shaft Q due to the smaller rotation of the rotating body J.

The structure shown in FIG. 28 (c) is obtained by replacing the spring V and the link S in the structure shown in FIGS. 28 (a) to 28 (c). One end of the springs V1, V2 is connected, and the other end of the springs V1, V2 is connected to one end of the links S1, S2. FIG. 28 (c) shows the fully opened state as shown in FIG. 28 (a), and the structure shown in FIG. 28 (c) has the same effect as described in FIGS. 28 (a) to 28 (c). Can be obtained.
In the structure shown in FIG. 28C, the hit Gs is provided not on the rotating body J but on the plate W. As in the case of FIGS. 28A to 28C, the link S2 hits from the time of full opening to just before closing and is brought into contact with G2 so as to keep the end Sv2 at the position of the rotation axis Q.

In the spring mechanism shown in FIG. 28, the rotation of the rotating body J until the fulcrum SV of the spring is separated from the rotation axis Q and the rotation moment about the rotation axis Q is greatly increased is as small as possible, ie, sealed as much as possible. In order to reduce the rotation of the door, the larger the distance between the rotating shaft Q and the connecting shaft SJ2, the better. However, the device needs to be enlarged. In FIG. 29, a large rotational force is instantaneously applied to the door during sealing without enlarging the apparatus.
The link S, the rotary shaft I spring V and its fulcrum SV, SW shown in FIG. 29 perform the same operation on the link S2, the rotary shaft SJ2 spring V2 and its fulcrum SV2, SW shown in FIG. 28, respectively. The wheel B is attached to the link S. In FIG. 29, instead of the hit Gs shown in FIG. 28, the circumferential sliding surface K2 centering on the rotation axis Q brings the end Sv to the position of the rotation axis Q. It plays the role of fastening.

As shown in FIGS. 29A and 29B, the wheel B moves along the circumferential sliding surface K2, so that the fulcrum SV of the spring V is held at the position of the rotation axis Q. Further, as shown in FIG. 29 (b), even if the wheel B moves away from the sliding surface K2, the wheel B moves along the concave surface of the sliding surface K1, and the wheel B slides near the end point of the sealing operation in FIG. 29 (c). The spring fulcrum SV is greatly pulled away from the rotation axis Q away from the moving surface K1.
As shown in FIG. 29 (b), before the fulcrum SV of the spring is separated from the rotation axis Q, the axis line of the link S and the axis line of the spring are bent, and as shown in FIG. It becomes a straight line. Thus, when the link S and the spring suddenly become a straight line, the distance S between the action line F of the force of the spring V and the rotating shaft instantaneously shows the maximum value, so that the rotational moment around the rotating shaft also causes the door to close. It occurs instantaneously at the end. That is, the force of the spring V acts only on a slight rotation of the door on which the latch operates.

When the wheel B moves on the sliding surface K1K2, the rotational speed of the rotating body J is reduced by rolling friction, but when the sealing force is finally applied, the spring V is released from these frictional resistances and sealed. It will show you all the power you can have. When the wheel B moves on the sliding surface K1, the rotational speed of the door is reduced. Further, when the wheel B moves on the sliding surface K2, the rotational speed of the door is decelerated just before closing, and temporarily stops. As shown in FIG. 28, the end Sv of the spring is held at the position of the rotation axis Q by the contact Gs, and the end Sv of the spring is moved to the rotation axis Q by the sliding surface K2 as shown in FIG. If it is kept in position, the door can be rotated while decelerating and the door can be tightly sealed simply by attaching the drive part of this spring structure to the door.
In FIG. 29 (c), the arrow → b indicates the moving direction of the wheel B when the closed door is opened, and the wheel B moves on the inner convex surface of the sliding surface K1 when the door is closed. When opening, the wheel B moves on the outer convex surface of the sliding surface K1.

As shown in FIGS. 29D and 29E, the rotating shaft Q shown in FIGS. 29A and 29B is composed of a circular rod M and a cylindrical bearing N through which the circular rod M penetrates. When the rotating body J is attached to the end of the circular rod M away from the bearing N and the spring force is applied to the end of the circular rod M, the concentrated load acts on the end of the cantilever. On the other hand, the circular rod M is bent and causes friction with the cylindrical bearing N through which the circular rod M passes. As shown in FIGS. 29A and 29B, the rotation of the rod M is resisted and decelerated while the end Sv is held at the position of the rotation axis Q.
The friction between the circular rod M and the bearing N increases as the distance Lm from the cylindrical bearing N to the end of the circular rod M on which the spring force acts increases. The rotational speed of the door can be adjusted by adjusting the distance Lm. If the rotating shaft Q shown in FIG. 28 is a cylindrical bearing N and a circular rod M shown in FIGS. 29 (d) and 29 (e), the rotation of the rotating shaft Q rotating only by this spring is transmitted to the rotation of the door. By simply attaching the drive part of the spring structure to the door, the door can be rotated while decelerating and the door can be tightly sealed.

Other examples of the “spring that suddenly generates a large force at the moment when the door is sealed” shown in FIG. 29 are shown in FIGS.
FIG. 30 shows the tangential movement of the circular motion around the connection axis Sj of the link S as in FIG. 29, and the wheel Bs attached to the tip of the link S has a circumferential sliding surface around the rotation center Q. It is blocked by moving along the upper Kw, and the fulcrum Sv of the spring is kept at the position of the rotation center Q.
In the case of FIG. 29, the wheel Bs moves along the inner side of the arc of the sliding surface Kw, whereas in FIG. 30, the wheel Bs moves along the outer side of the arc of the sliding surface Kw. When the wheel Bs changes to the sliding surface Kw, the fulcrum Sv of the spring is pulled to the position of the rotation center Q.
In the case of FIG. 29, it rotates while shortening the length of a spring, and in the case of FIG. 30, it rotates while extending the length of a spring. The rotation speed of the rotating body J is accelerated in the case of FIG. 29 and decelerated in the case of FIG.

In FIG. 31, an arc sliding surface Ks centered on the fulcrum Sv of the spring is provided at the tip of the link S, and the wheel Bw moves along the sliding surface Ks, so that the connection axis Sj of the link S is centered. The movement in the tangential direction of the circular motion is prevented.
32 and 33 are different from FIGS. 29, 30, and 31, the spring V is rotatably supported around the rotation fulcrum Sj of the rotating body J, and the link S is rotatably supported around the rotation fulcrum Sw. . When the door is opened from the state where the door is completely closed, the rotating body J rotates in the opposite direction to ⇒, and the wheel B passes on the surface on the opposite side to the surface that is in contact with the sliding surface K when the door is closed. To do. The surface where the wheel B contacts the sliding surface K when the door is closed is the inner side in FIGS. 29, 32 and 33 and the outer side in FIGS.
When the door is opened, the wheel B passes the outside in FIGS. 29, 32, and 33, and passes the inside in FIG. In all cases of FIGS. 29 and 30 to 33, when the door is opened, it passes through a route different from the route when the wheel B is closed, and in either case, it passes while extending the spring. You can also open the door with less resistance

In FIG. 31, the wheel Bw is attached to the tip of an arm Ab that rotates around the rotation axis Ia. When the door is closed, the arm Ab rotates in a direction that hits Gb, and when the door is opened, it rotates in a direction away from Gb. In the case of FIG. 31, when the door is opened, the fulcrum Sv of the spring returns to the position of the rotation center Q while keeping the spring and the rotating body in a straight line. When the door closes and the spring fulcrum SV moves away from the center of rotation Q and the door hits the door in a moment, the door rotates and the spring expands and contracts slightly, but in this case the door is moved away from the door. When opening, in the case of FIG. 33, the rotation of the door and the expansion and contraction of the spring are slight.

In the range of Y ± 0 to Y + 30, that is, the range where the link S and the contact Gj are in contact, there is no portion where the link S and the contact Gj of the sliding surface K are in contact. The length of the sliding surface is shortened so that when the door is opened in this range, the sliding surface can move to the contact surface side when the wheel B is closed. Further, when closing the door in the range of Y-30 to Y ± 0, even if the spring force increases continuously, the amount of rotation of the door is small, so that the impact when accelerating or closing is not a problem. There is no difference in the force of the spring that presses the door against the door.

34 to 37 and 79 to 82, “means including a cam wheel and a cam body sliding surface” makes it possible to freely adjust the force acting on the door.
A wheel that moves down a sliding surface having a downward slope has a small force acting in the moving direction even if the force pressing the sliding surface is large, and the rotational resistance around the rotation axis of the wheel resists the movement of the wheel. The force that presses the sliding surface is the force that seals the door, and the force that acts in the moving direction is used to rotate the door. Even when the door is closed, the force acting on the door is small when opening the door, the force acting at the time of sealing is large, and the ratio of the magnitude of the former force and the latter force can be ensured even if the rotational resistance is large. . The speed of the wheel moving along the sliding surface can be adjusted by changing the gradient of the sliding surface or by changing the material of the wheel from a steel wheel with a bearing to a rubber wheel.
In general, the means to change “physical property that expands and contracts in an instant” to “physical property that expands and contracts over time” is a moving means that involves friction. In a door that uses a spring as a driving means, "Wheel to do" is a means to change the physical properties of the spring.
34 to 37 and 79 to 82, the means is “a cam body rotating around a drive shaft, a cam body sliding surface provided on the cam body, and a wheel body rotating around a driven shaft. And a wheel mounted on a rotation spindle provided at the tip of the wheel body, wherein the wheel moves along the cam body sliding surface, The intermediate portion has a constant distance between the perpendicular line standing on the sliding surface of the cam body through the “contact point between the wheel and the sliding surface of the cam body” and the driven shaft or the driving shaft. An opening / closing device provided with a rotation mechanism.
A cam body that rotates about a drive shaft, a cam body sliding surface provided on the cam body, and a wheel that moves along the cam body sliding surface, the wheel moving away from or approaching the drive shaft. A moving device for moving the cam body in a direction, wherein the shape of the sliding surface of the cam body passes through a “contact point between the wheel and the sliding surface of the cam body”, and a vertical line standing on the sliding surface of the cam body, the drive shaft, A moving device characterized by a constant distance between the two.
“Rotating mechanism characterized in that the shape of the sliding surface of the cam body is an involute vortex” or a moving device.

As shown in FIG. 35, the former is a means for providing a constant rotational force to the cam wheel rotating shaft, and the latter is a cam wheel rotating shaft, and is a means for providing a constant rotating force to the cam wheel rotating shaft. The constant pressing force acting on the slab is converted into a constant rotational force. The former is also compression means for rotating the cam body sliding surface by providing a constant pressure. FIG. 79 shows an example in which the pressing force is not constant with changes in the position of the cam wheel on the sliding surface of the cam body and the spring force. “The above-mentioned constant distance” is corrected to “substantially constant distance”. become.
As shown in FIGS. 37 and 80, the latter is a means for providing a constant pressing force to the cam wheel by applying a constant rotational force around the drive shaft, The constant pressing force acting during the period is converted into a constant rotational force. When the vortex line shape is an involute vortex line, it is a moving means for moving the cam wheel by a constant stopping force, and can be applied to industrial fields other than doors. In general, the force required to move an object up and down changes in the process of moving the object up and down, and by making the magnitude of the force to move the object up and down constant, the maximum value of the force to move the object up and down It can be made smaller.
82 and 83 show an embodiment of an opening / closing device having the former rotation mechanism. FIG. 82 shows a case where the cam body rotation shaft relatively revolves around the cam wheel rotation body rotation axis in FIG. 34, and FIG. 81 shows a case where the cam body rotation shaft relatively moves around the cam wheel rotation body rotation shaft in FIG. It is an example in the case of revolution. The embodiment of FIGS. 81 and 82 is a sliding surface that is rotatably supported as shown in FIGS. 46, 49, and 57. The sliding surface of FIGS. 81 and 82 revolves while rotating, and the wheel moves. 46, 49, and 57, the sliding surface revolves without rotating, and the wheel does not move and keeps the rotating force constant. The sliding surfaces 49 and 57 suddenly rotate when sealed, and the wheels held near the door pivot suddenly move far away from the door pivot.

When applied to the cam body sliding surface and the cam wheel door, the rotating means is within the range (A). In the range (A), most of the spring force is a pressing force that works perpendicularly to the cam body sliding surface, and part of the force acts in the direction of movement of the wheel and parallel to the cam body sliding surface. The force in the moving direction of the wheel is the driving force for rotating the door, and even if the spring force is strong, the force acting on the door is weak, not only rotating the door slowly, but also lightening the door when opening the door I try to feel it. That is, in the range (A), the door is rotated by a part of the force while preserving most of the force of the spring.
In the range (A), the cam wheel moves along the sliding surface of the cam body as the door rotates. In the former case, the cam body rotates, and in the latter case, the cam wheel rotating body rotates little and the spring expands and contracts. Few. Therefore, the strain energy of the spring given to the rotational movement of the door is small and the acceleration of the rotational movement of the door is small. When switching from the range (A) to the range (I), the cam wheel moves away from the intermediate portion of the cam body sliding surface and moves to the end closest to the rotating shaft of the cam body sliding surface. The gradient of the cam body sliding surface in the moving direction of the cam wheel changes abruptly, and the movement of the cam wheel and the expansion and contraction of the spring increase with a small rotation of the door. In the range of (ii), all of the spring force is the force that seals the door.

FIGS. 34 to 37 are operation explanation plan views of “a rotation transmission device including a cam body sliding surface K and a cam wheel B moving along the cam body sliding surface K”, and FIGS. 34 to 36 show “the cam body sliding surface K is a cam body”. A rotation transmission device that rotates in the direction of arrow A in the figure about the rotation axis Qk, presses the cam wheel B, and rotates the cam wheel rotation body Jq in the direction of arrow B in the figure about the cam wheel rotation body rotation axis Qj. 37, “the cam wheel rotating body Jq rotates around the cam wheel rotating body rotation axis Qj in the direction of arrow A in the figure, and the cam wheel B presses the cam body sliding surface K to The rotation transmission device rotates the body sliding surface K in the direction indicated by the arrow B in the figure around the cam body rotation axis Qk.
34 to 37, the cam body KK is rotatably supported around the cam body rotation axis Qk, and the cam wheel rotation body Jq is rotatably supported around the cam wheel rotation body rotation axis Qj. The cam wheel B is attached to a rotation support shaft Ib provided at the tip of the cam wheel rotating body Jq, and the cam wheel B moves along a cam body sliding surface K provided on the cam body KK.
The curve of the sliding surface of the body described with reference to FIGS. 34 and 35 is the cam body sliding surface K shown in FIGS. 24 to 26, and the curve of the sliding surface of the body described with reference to FIG. 36 is the cam body shown in FIG. The curved surface of the sliding surface K described with reference to FIG. 37 is the sliding surface of the cam body KK1 shown in FIG.

The shape of the cam body sliding surface of the rotation transmission device of FIGS. 34 to 36 is “a shape in which the line of action Fb of the force that the cam body sliding surface K presses the cam wheel B maintains a certain distance from the rotating body rotation axis Qj”. The shape of the sliding surface of the cam body of the rotation transmission device of FIG. 37 is “the action line Fb of the force by which the cam wheel B presses the sliding surface K of the cam body B maintains a constant distance from the cam body rotation axis Qk. Shape ".
34 to 37, at an arbitrary contact b between the wheel B and the cam body sliding surface K, the action line Fb of the pressing force acting on the wheel B is maintained at a constant distance from the cam wheel rotating body rotation axis Qj. At any position on the body sliding surface K, the perpendicular line T standing on the cam body sliding surface K is tangent to the common virtual circle R. That is, the rotational force acting on the cam wheel rotating body Jq is the same regardless of where the door is opened.
In a door opening and closing device having a vertical rotation axis, a “force slightly exceeding the maximum static frictional force acting on the door pivot axis O” acts to rotate the door in a state close to a balanced state. The cam body sliding surface shown in FIG. 5 is a means for providing “a rotational force slightly exceeding the maximum static frictional force acting on the pivot axis O of the door”.

As shown in FIGS. 35 to 37, the shape of the sliding surface of the cam body is different between the intermediate portion K and the end portion Kc, and “the action line Fb of the force by which the cam wheel B presses the cam body sliding surface K” The distance from the axis Qk is kept small and constant at the middle portion and greatly increased at the end portion.
FIG. 35B shows a cam body sliding surface K0 that presses the cam wheel B0 that is close to the cam body sliding surface K90 that presses the cam wheel B90 that is far from the cam body rotation axis Qk.
Considering the cam body sliding surface K as “the lever that presses the cam wheel B with the cam body rotation axis Qk as a fulcrum”, the “force that the cam body sliding surface K presses the cam wheel B” is the cam body rotation axis Qk. When the cam wheel B moves along the cam body sliding surface Kc, it does not change and remains constant when moving along the cam body sliding surface K from the position far from the position to the near position. Become.
That is, the cam wheel B moves along the cam body sliding surface K and does not function as a lever in the “range from fully open to immediately before closing (A)”, and the cam wheel B follows the cam body sliding surface Kc. It functions as a lever in the “range from just before closing until closing” (i).
Reduce the radius of the common virtual circle R to reduce the "distance between the pressing force action line Fb and the cam wheel rotor rotation axis Qj", and increase the strength of the spring so that the door can barely rotate. Then, a big force comes to act at the time of sealing. That is, by changing the shape without changing the size of the cam body sliding surface shown in FIGS. 35 to 37, it becomes a device that outputs a large sealing force, and the action line Fb of the pressing force is extremely applied to the cam wheel rotating body rotation axis Qj. By bringing them closer, the device can be made smaller.

Next, differences and common points between the rotating mechanism shown in FIGS. 35 to 37 and the embodiments shown in FIGS. 6 to 8 will be described.
6 to 8 show an embodiment in which the wheel B presses the sliding surface K, the wheel B moves along the fixed sliding surface K, and the door rotates. The rotating mechanism shown in FIG. 2 fixes the wheel B to the door and rotates the sliding surface K so that the sliding surface K moves along the wheel B, the sliding surface K presses the wheel B, and the door rotates. This is an embodiment.
6 to 8, the wheel B remains in the vicinity of the pivot axis O of the door and does not move along the sliding surface K in the “range from fully open to just before closing (A)”. Rotate relatively. The distance Lf between the “operation line of the force Fb that the wheel B presses the sliding surface K” and the pivot O of the door is kept constant. In the “range from just before closing to the closing time (i)”, the wheel B staying in the vicinity of the door pivot O moves to a position away from the door pivot O. At this time, the sliding surface K does not rotate relatively. The distance Lf between the “operation line of the force Fb that the wheel B presses the sliding surface K” and the pivot axis O of the door suddenly changes.
On the other hand, in the embodiment of FIGS. 34 to 37, the wheel B moves along the sliding surface K in the “range from fully open to just before closing (A)”, and the sliding surface K almost rotates. Instead, the distance Lf between the “operation line of the force Fb that the wheel B presses the sliding surface K” and the pivot O of the door is kept constant. In the “range from immediately before closing to the closing time (i)”, the wheel B moves while greatly changing the moving direction at the end of the sliding surface K, and the sliding surface K rotates greatly. The distance Lf between the “operation line of the force Fb that the wheel B presses the sliding surface K” and the pivot axis O of the door suddenly changes.

Thus, there is a large difference in the movement of the wheel between the embodiment of FIGS. 6-8 and the embodiment of FIGS. 34-37, and the embodiment of FIGS. Means ”and“ switching means ”in which the wheel moves greatly. In the embodiments of FIGS. 34 to 37,“ rotating means in the range (a) ”in which the wheel moves greatly and“ switching means ”in which the wheel does not move. Prepare.
However, in both the embodiment of FIGS. 6 to 8 and the embodiment of FIGS. 34 to 37, the “line of action of the force Fb that the wheel B presses the sliding surface K” does not move from the vicinity of the pivot axis O of the door. ”Rotating means” and “switching means” in which the action line moves greatly. Further, the “switching means” has a common point, and the wheel B operates greatly in the embodiments of FIGS. 6 to 8, and the sliding surface K operates greatly in the embodiments of FIGS.
That is, by moving the action line of Fb, “two ranges in which different magnitudes of force act and can be clearly distinguished” are realized, and when the magnitude of the force changes, the driven rotor (door D) is slightly changed. The open / close device (link device) operates greatly with proper rotation. The magnitude of the force acting on the driven rotating body and the change thereof are the same, and the driven rotating body performs the same operation.

The cam body sliding surface shape that makes the force acting on the door constant will be described.
The shape of the concave cam body sliding surface of FIG. 34 will be described with reference to FIG. 35A, and the shape of the convex cam body sliding surface of FIG. 36A will be described with reference to FIG.
In FIG. 35 (a) and FIG. 36 (b), points bi (i = 0, 1, 2,...) Are equally divided on a circle Rb centered on the cam wheel rotating body rotation axis Qj. A point bi (i = 0, 1, 2,...) Is a contact point that moves from time to time between the cam body sliding surface K and the cam wheel B. A tangent line Ti (i = 0, 1, 2,...) Passing through the point bi is in contact with a contact point ai (i = 0, 1, 2,...) Of a virtual circle Ra centering on the rotating body rotation axis Qj. . An arc Ri (i = 0, 1, 2,...) Is an arc having the above-mentioned contact ai as a center and a radius abi, and the cam body sliding surface that contacts the cam wheel B moving on the circle Rb from time to time. It is the periphery of the contact part of K.
Since the circle Ra and the circle Rb are concentric circles, the lengths aibi of the tangent line Ti are all the same, and the arc angles of the arc Ri and the circle Rb are all the same. That is, the sliding surface K always maintains a constant gradient with respect to the moving direction of the cam wheel B.
Here, the circles Ra and Rb are concentric circles, and the radii a0b0, a1b1, a2b2,... Have the same length, so that the broken lines aibiRi are all congruent. When the polygonal line aibiRi (i = 0, 1, 2,...) Is rotated around the cam body rotation axis Qk and moved to jikiKi (i = 0, 1, 2,...), The circles R0, R1. , Rb2,... Form one sliding surface K0K1K2K3K4K5 continuous with R5.

In FIG. 35 (a), arc R7 is an arc starting from point a7 and starting from point b7, and arc R6 is an arc starting from point b6 and starting from point b6. The arc R6 is rotationally moved about the cam body rotation axis Qk to be K6, and is continued to the starting point b7 of the arc R7. The arc R7 and the arc R6 form one arc, and the start point b6 moves to the start point k6 of the arc K6 that has been rotated. When the arc R5 is further rotated about the cam body rotation axis Qk so as to be continuous with the start point k6 of the arc K6, the arc R7, the arc R6 and the arc R5 form one arc, and the start point b5 is rotated. Move to the starting point k5 of the moved arc K5. In this way, the cam body sliding surface KA is drawn by successively continuing K5, K4, K3,. A cam body sliding surface KA in the figure is a cam body sliding surface K that rotates about the cam body rotation axis Qk, and is the cam body sliding surface K when it contacts the cam wheel B at a point b7.
The same applies to FIG. 36 (b), and the arc R4 centered on the contact point a4 passing through the point b4 is rotated about the cam body rotation axis Qk to reach the starting point b5 of the arc R5 centered on the contact point a5. When they are continuous, the arc R5 and the arc R4 form one arc, and the start point b4 moves to the start point k4 of the arc K4 that has been rotated. The continuous arc is an arc K4, the arc R3 is moved to the starting point k4 of the arc K4, the arc K3 is continued, the arc R2 is further moved, and the arc K2 is continued to draw the shape of the cam body sliding surface KA. Is done. In this way, the cam body sliding surface KA is drawn by successively continuing R5, K4, K3,. The cam body sliding surface KA in the figure is a cam body sliding surface K that rotates about the cam body rotation axis Qk, and is the cam body sliding surface K when contacting the cam wheel B at the point b5.

35 (a) and 36 (b), the direction of the tangent line T is opposite to each other at the contact point a between the tangent line T and the virtual circle Ra. In FIG. 35 (a), FIG. ), As the radius of the virtual circle increases, the drawn sliding surface KA moves away from the circle Rb, and the gradient of the sliding surface K with respect to the moving direction of the cam wheel B increases. In FIG. 35 (a), the sliding surface KA is moved away from the outside of the circle Rb, and the drawn vortex is more curved. In FIG. 36 (b), the sliding surface KA is moved away from the inside of the circle Rb, and the drawn vortex line is closer to a straight line.
In both FIG. 35 (a) and FIG. 36 (b), when the radius of the imaginary circle is reduced, the drawn sliding surface KA approaches the circle Rb, and the sliding surface K of the cam wheel B moves in the moving direction. The slope decreases.
When the drawn sliding surface KA is a circle, neither the cam body sliding surface K nor the cam wheel rotating body Jq rotates, and the action line Fb of the force with which the sliding surface presses the wheel is the cam wheel rotating body rotation. It passes through the axis Qj and matches the axis of the cam wheel rotor.
The drawn sliding surface KA approaches the circle Rb, regardless of how large the rotational force acting around the cam body rotation axis Qk is. For example, in FIG. 35 (b), even if the pulling spring V is strengthened and the force for sealing the door is increased, the rotation of the door is not transmitted. Conversely, even if the rotational force acting around the rotating shaft Qj of the cam wheel rotating body is small, the cam wheel B can move on the sliding surface K, and a large axial force is transmitted to the sliding surface K. Become.

For example, in FIG. 35B, the force of the tension spring V decreases as the cam body sliding surface K rotates, but as the cam wheel B moves along the sliding surface K and approaches the cam body rotation axis Qk, the tension spring V Since the force of V is greatly converted into “the force Fb that the sliding surface presses the wheel”, the “force Fb that the sliding surface presses the wheel” is corrected to a constant value, and the cam wheel rotating body Jq is fixed. Can be designed to work with rotational force. This rotation mechanism is a means that keeps the door rotating with “a rotational force slightly exceeding the maximum static frictional force acting on the pivot axis O of the door”.
Conversely, when a constant rotational force acts around the cam wheel rotating body rotation axis Qj, the cam wheel B moves on the sliding surface K while transmitting a constant axial force to the sliding surface K. This rotating mechanism is means for keeping the rotating body rotating at a constant rotational force such that the rotational moment acting around the cam body rotation axis Qk changes as the cam wheel B moves on the sliding surface K. For example, for a lid that has a horizontal rotation axis and swings between a standing position and a lying position, the center of gravity moves away from the rotating axis in the horizontal direction as the lid rotates from the standing position to the lying position. Therefore, if the cam wheel B is also moved on the sliding surface K away from the rotation axis, the lid can be continuously rotated with a constant rotational force.

FIG. 37 shows a rotation transmission device in which the cam wheel B presses the cam body sliding surface K and rotates the cam body as shown in FIG. The action line Fb of the pressing force acting on the wheel passes through the rotation axis Ib of the wheel and the “contact point b between the cam wheel B and the cam body sliding surface K” and always maintains a constant distance from the cam body rotation axis Qk. “The shape of the cam body sliding surface in which the line of action of the pressing force acting between the cam wheel and the cam body sliding surface keeps a constant distance from the cam body rotating shaft” is shown in FIG. Drawing is performed in accordance with the drawing method described in FIGS. 35 (a) and 36 (b).
Regardless of the position of the cam wheel B on the cam body sliding surface K, the action line Fb is in contact with the virtual circle Ra whose center is the cam wheel rotating body rotation axis Qj, and the action line Fb is at the virtual circle Ra and the contact point a. It touches.
As shown in FIG. 37 (b), “the contact point b between the cam wheel B and the cam body sliding surface K” moves on a circle Rb about the cam wheel rotating body rotation axis Qj. When the body sliding surface K contacts the contact bi (i = 1, 2, 3,...), The cam body sliding surface continuous to the contact bi is “the contact a between the action line Fb and the virtual circle Ra”. Is a circular arc Ri (i = 1, 2, 3,...).
A circle Roi (i = 1, 2, 3,...) Is a circle that passes through the contact point bi with the cam body rotation axis Qk as the center, and intersects with the arc Ri (i = 1, 2, 3,...). Intersect. When the arc bici divided by the circle Roi is sequentially rotated around the cam body rotation axis Qk so as to be continuous with R0, one curve R0K1K2K3... Is formed. This curve is a sliding surface K shown in FIG.

The circles Ro1, Ro2, and Ro3 shown in FIG. 37 are concentric with the virtual circle Ra, and no matter where the point bi is located on the circles Ro1, Ro2, or Ro3, the tangent line Ti starting from the point bi and the starting point bi All the continuous arcs Ri are congruent, and the shape of the formed sliding surface K is an involute vortex, and is constant regardless of the position of the point bi on the circles Ro1, Ro2, and Ro3. . That is, the shape of the sliding surface K is uniquely determined by the size of the virtual circle Ra and is not related to the cam wheel B.
35 (a) and 36 (b), the center of the virtual circle Ra is the cam wheel rotating body rotation axis Qj. In FIG. 37 (b), the center of the virtual circle Ra is the cam body rotating axis Qk. The center of the virtual circle Ra coincides with the center of rotation when the arc Ri moves to the arc Ki. The involute vortex K indicates that the cam wheel is positioned around the cam body rotation axis Qk when the pressing force acting between the cam wheel and the cam body sliding surface is constant. However, when the constant rotational force is applied around the cam body rotation axis Qk, the force with which the cam body sliding surface presses the cam wheel is constant.
When a constant pressing force is applied to the cam body sliding surface shown in FIG. 37, as long as the cam wheel B is in contact with the cam body sliding surface, no matter how the cam wheel B moves in the space, It rotates with a constant rotational force. Further, the cam wheel B on which a constant pressing force acts moves by a cam body sliding surface that rotates with a constant rotational force. In this case as well, a constant pressing force acting on the cam wheel and a constant rotational force acting on the cam body are suspended regardless of the movement trajectory of the cam wheel B. The rotation transmission device shown in FIG. 37 is also a moving device.

Next, the cam body sliding surface shape that allows a strong force to act on the door only when the door is sealed will be described.
35 (b), 36 (a), and 37 (a), “the portion of the cam body sliding surface K close to the cam body rotation axis Qk” is a straight line Kc or a convex surface Kd, immediately before the door is closed. When the cam wheel B is in the “portion close to the cam body rotation axis Qk”, the distance between the action line of the force that the cam wheel presses the cam body sliding surface and the rotation body rotation shaft suddenly changes greatly, and the cam body The sliding surface presses the cam wheel with a strong force. A strong force is applied to the door only when the door is sealed in this way.

In FIG. 34, when the cam body KK rotates in the direction of arrow A in the figure, the cam wheel B revolves around the cam wheel rotating body rotation axis Qj in the direction of arrow B in the figure. FIG. 34 (a) shows a state where the door is fully opened, FIG. 34 (c) shows a closed state, and FIG. 34 (b) shows a state in the middle thereof.
The tension spring V has one end connected to the connecting shaft Sk of the cam body KK and the other end fixed to the connecting shaft Sw, and is extended and contracted along a circumferential guide rail Ks centered on the rotating shaft Qk. .

“The force Fb by which the cam body sliding surface K presses the cam wheel B” varies depending on the position of the cam wheel on the cam body sliding surface K and also by the rotational force Mk acting around the cam body rotation axis Qk. In order to make the pressing force Fb constant, the guide rail Ks adjusts the length of the tension spring V accompanying the rotation of the cam body and the distance between the action line Fv of the tension force of the tension spring V and the rotation axis Qk. .
As the door is closed from the fully open state, the length of the pulling spring is reduced, the spring force is weakened and the rotational moment Mk acting on the cam body KK is reduced. The moving surface K is adjusted so that the force Fb for pressing the cam wheel B is constant.
FIG. 35 defines the shape of the sliding surface K of the cam body KK that gives a constant rotational moment to the cam wheel rotating body Jq, assuming that a constant pressing force Fb acts on the cam wheel B.

As shown in FIG. 34 (a), “Mj working around the cam wheel rotating body rotation axis O” increases as the cam wheel rotating body rotation axis Qj moves away from the rotating body rotation axis Qk, and decreases as it approaches. Qjj shown in FIG. 34 (a) indicates a position when the cam wheel rotating body rotation axis Qj is moved away from the rotating body rotation axis Qk, and “cam wheel rotating body rotation axis Qj is moved away from the rotating body rotation axis Q”. The distance Lfjj "between the force action line Fb and the center of rotation is greater than the previous distance Lfj". For this reason, “Mj working around the cam wheel rotating body rotation axis O” can be increased by moving the cam wheel rotating body rotation axis Qj away from the rotating body rotation axis Qk, and can be decreased by approaching it.

The curve of the cam body sliding surface indicated by the dotted line in FIG. 35 (a) is a curve that makes the distance between the line of action of the pressing force acting on the cam wheel B and the rotation axis O of the cam wheel rotating body Jq constant, Even when the door is sealed, the same rotational force as that during rotation is output, so the force for sealing the door is insufficient. FIG. 35 (b) illustrates a curve in the vicinity of the starting point of the cam body sliding surface that is continuous therewith.

As shown in FIG. 35 (b), when the linear sliding surface KC indicated by the two-dot chain line continues in the “near the starting point of the curve of the cam body sliding surface K”, the sliding surface KC becomes the cam wheel B. The distance between the line of action of the working pressing force and the rotating shaft of the cam wheel rotating body Jq increases, and the door is tightly sealed.
In addition, when the convex sliding surface KD indicated by the two-dot chain line continues, the sliding surface changes from a concave surface to a convex surface, and “the action line of the pressing force acting on the cam wheel B and the rotation of the rotating body A” The “distance with respect to the axis O” is further larger than when the linear sliding surface KC is continuous.
Even if the door closing speed is low, it closes while accelerating, but decelerates immediately before closing the door by continuing the arc sliding surface KA indicated by the solid line near the starting point of the curve of the cam body sliding surface K. Further, the linear sliding surface KC and the convex sliding surface KD are made continuous so as to be tightly sealed.

In the tension spring V shown in FIG. 35 (b), one end is close to the cam body rotating body Q and the other end is located far from the cam body rotating shaft Q of the cam body KK. By attaching, the expansion and contraction of the spring is reduced.
The curve of the cam body sliding surface described in FIGS. 34 and 35 is the cam body sliding surface K shown in FIGS. 24 to 26, and the curve of the cam body sliding surface described in FIG. 36 is the cam body shown in FIG. 37, the curve of the cam body sliding surface described in FIG. 37 is the sliding surface K of the cam body KK1 shown in FIG.

38 to 40 are plan views for explaining the operation of the connecting portion PP of FIG.
FIG. 38 is an operation explanatory view of the case where the end of the link A is bent into an L shape as in the case of FIG. 13. FIG. 38 (a) shows a state before the axis of the link A passes over the rotation axis Q. FIG. 38B shows a state after passing through. The connection points P, PP, and C of the two links A and AA are always on the same straight line ZZ, and the axis lines of the two links A and AA are not bent. The axis of the link A is a straight line passing through the connecting shaft P and the connecting shaft PP.
In FIG. 38 (a), when the tip of the link A is not bent into an L shape, the link core PP does not pass over the rotation axis Q, and the connection axis PP is “the connection between the rotation axis Q and the door. The rotating body J and the link A rotate together without entering the region (a) that does not include the door pivot O at the straight line Z connecting the axis C, and the axis of the two links A and AA is rotated. Bends. In order for the axis of the link A to pass over the rotation axis Q, the tip of the link A must be bent into an L shape, or the link A must pass over the cut end of the rotation axis Q. .
In FIG. 38 (b), a circle Rc is a circle centered on the connection axis C through the point P, and a circle Rq is a circle centered on the rotation axis Q through the point P with the straight line ZZ as the boundary (e.g. On the) side, the circle Rc is outside the circle Rq. This means that the “distance between the rotation axis Q and the connection axis C” decreases on the (b) side with the straight line ZZ as a boundary, and the axis of the links A and AA bends. is doing.
That is, “the phenomenon in which the axis of the links A and AA is bent” means that the links A and AA may be performed before they come into contact with each other.

When the shaft cores of the two links A and AA rotate while maintaining a straight line and pass over the rotation axis Q just before closing, before the link A and the rotation body J are united, the arrow A in the drawing of the rotation body J The rotation in the direction is a movement to increase the “distance between the rotation axis Q and the connection axis C” if the axis lines of the links A and AA are kept in a straight line, and to rotate the door in the opening direction. However, since the links A and AA are bent, the connecting shaft PP rotates about the rotation axis Q in the direction of the arrow C in the figure, and closes the door while reducing the “distance between the rotation axis Q and the connection axis C”. Rotate in the direction. Eventually, the link A and the rotating body J are united and the connecting point PP has entered the “post-border area”, so the two links A and AA are bent and rotated in the direction to open the door. After that, the door rotates in the closing direction and closes.
The door reverses the rotation direction twice just before closing, and the rotation speed of the door becomes zero each time the rotation direction reverses. In other words, it is a movement that not only stops the moving door but also moves the stationary door, and it takes time to eliminate the dynamic inertia, and it takes time to eliminate the static inertia, so the direction of movement is reversed. Every time you do it, it slows down.

After the connecting point PP enters the “post-border area” and the link A and the rotating body J are integrated, the inertial force acting on the door exceeds the rotating force of the rotating body J, and the door is in the direction of arrow B in the figure. When the door D is to be rotated, the door D rotates in the direction indicated by the arrow B in the figure, and the connecting shaft PP rotates about the rotation axis Q in the direction indicated by the arrow C in the figure. The rotational force acting in the direction of the arrow C in the figure about the rotation axis Q rotates the integral rotating bodies J and AA in the direction opposite to the arrow A in the figure.
The rotation of the connecting shaft P in the direction opposite to the arrow A in the figure is a movement that increases the “distance between the rotating shaft Q and the connecting shaft C”, and is a movement that moves the link A away from the rotating body J. However, the movement in which the connecting shaft PP rotates in the direction indicated by the arrow C in the drawing is the movement in which the link A is brought closer to the rotating body J, and the link device cannot be rotated. That is, when the door closes suddenly due to a strong wind, the door stops immediately before it closes and stops still in an open state.
The door of the present invention has a “function to stop before the door covered with strong winds is closed”, and has a function equivalent to “a door closer using a hydraulic cylinder”, thereby preventing a finger jamming accident. .

Further, if the door D is added in the direction in which the door D is opened while the connecting point PP has entered the “post-border zone”, the connecting shaft PP rotates about the rotation axis Q in the direction opposite to the arrow C in the figure. The rotational force acting in the opposite direction to the arrow C in the figure about the rotation axis Q rotates the integral rotating bodies J and AA in the direction of the arrow A in the figure, and brings the link A closer to the rotating body J. When the movement approaching the link A to the rotating body J is prevented by the contacting of the rotating bodies J and AA, “the rotation of the integrated rotating body J and AA in the direction of arrow A in the figure” is also prevented. Tip bent by connecting point PP of the link A as shown in FIG. 13 is unopenable as to open the door so as to penetrate the "cross-border after region".

The operation will be described with reference to FIG.
39 has the same structure as that of FIGS. 13 and 38, and the link A has its tip bent at a right angle. FIG. 38B shows a state where the rotating body J and the link A are separated from each other, that is, the “space between the rotating body J and the link A” shown in FIG. The connection shaft P and the connection shaft PP cross the “straight line Z passing through the rotation shaft Q and the connection shaft C” and both enter the “post-border boundary region”. In the case of FIG. 38 (b), when the links A and AA are not bent and keep a straight line before the rotating body J and the link A come into contact with each other, the door D is in the direction of arrow B in the figure. The movement of the connecting shaft PP close to the rotation axis Q due to the rotation and the movement of the connecting body PP moving away from the rotation axis Q due to the rotation of the rotating body J in the direction of arrow A in the figure interfere with each other. Suddenly stops. Sudden stoppage of the link device is the same as the door hitting the door just before, and no impact sound is generated, but the impact is applied to the device and the bolt on the mounting part of the device is pulled out. Take it.
In order to avoid such a collision, FIG. 39 differs from the embodiment of FIG. 38 in that the rotating body J and the link A are integrated to maintain a straight line immediately after the connecting shaft PP crosses the straight line Z. A and AA are bent so that the connecting shaft PP moves around the rotation axis Q in the direction opposite to the arrow C in the figure. Also, FIG. 39 shows that the movement after the connecting shaft PP crosses the straight line Z is made as small as possible by integrating the rotating body J and the link A with the space (a) shown in FIG. The degree of change in the direction of movement of the connecting shaft PP from the direction indicated by the arrow C in the drawing to the opposite direction is made as small as possible to make the above-mentioned collision “slow deceleration”. That is, the wider the “space (B) shown in FIG. 38B” when the rotating body J and the link A are integrated, the more gently “decelerate”.

The part indicated by the solid line in FIG. 39 (a) is the state immediately before the door is closed. A portion indicated by a dotted line indicates a state where the door is fully opened and a state where the door is closed. The rotating body J and the link A are in a state of being separated in the fully opened state and the middle of closing shown by the dotted line in FIG. 39A, and the connecting shaft P, the connecting shaft PP, and the connecting shaft C are in a straight line.
As the door is closed, the angle formed by the rotating body J and the link A on the connecting shaft P gradually decreases, and the rotating body J and the link A come into contact with each other immediately before the door is closed as shown by the solid line in FIG. The rotating body J and the link A are integrated. The connecting shaft P, the connecting shaft PP, and the connecting shaft C are in a straight line until the rotating body J and the link A come into contact with each other.

39 (b) shows a state in which the connecting shaft P, the connecting shaft PP, and the connecting shaft C are in a straight line when the rotating body J and the link A are united immediately before the door is closed, and the solid line shows a solid line. The illustrated portion shows a state in which the connecting shaft PP rotates around the rotating shaft Q and pulls the connecting shaft C after the rotating body J and the link A are integrated.
The portion indicated by the dotted line in FIG. 39B is a state where the connecting shaft PP has entered the “post-border region” across the “straight line passing through the rotating shaft Q and the connecting shaft C”, and the three points Q, PP, The straight line passing through “C” is “curved”, and when the rotating body J further rotates, it returns to the straight line and “curves”. The door rotates in the opening direction when returning from the “L” to the straight line, and the door rotates in the closing direction when turning from the straight line to the “U”. When the degree of bending to the “Koji” is small, the door is less rotated in the opening direction and less likely to collide.

In the process of closing the door by the rotation of the rotating body J, the door that rotates in the opening direction once rotates the rotating body J in the closing direction when the door is opened. In the process of closing the door, the state in which the connecting shaft PP is about to exit from the “post-border zone” coincides with the state in which the connecting shaft PP is about to enter the “post-border zone” when the closed door is opened. .
When the state where both the connecting shaft P and the connecting shaft PP are in the “post-border region” occurs in the process of closing the door, it also occurs when the closed door is opened. A door is a "door that does not open even if it tries to open".

The operation will be described with reference to FIG.
FIG. 40 solves the “defect that does not open from the closed state” of the door shown in FIG. 39. The structure of FIG. 40 is similar to the structure of FIG. 39, and the link A of FIG. Like link 39 of 39, it is made straight without being bent at the tip. In addition, the axis of the link A is prevented from passing over the cut end of the rotation axis Q. Therefore, the connecting shaft PP does not enter the “post-border area”, and the door does not rotate in the direction of opening once during the closing, nor does it suddenly stop during the rapid rotation.

In FIG. 40, the springs V are loaded so that the links A and AA are bent around the connecting shaft PP from when the door is fully opened until the rotating body J and the link A are integrated. Further, Gq is attached to the connecting shaft PP so that the links A and AA are not further bent at the connecting shaft PP.
In this way, as shown in FIG. 40 (a), when J and the link A are united immediately before closing, the straight line passing through the three points Q, PP, and C is bent into a "<" shape. As in the case, the connecting shaft PP enters the “post-border area” and rotates in the opening direction before the door is closed. It also stops suddenly during rapid rotation. The door of FIG. 40 is not a “door that cannot be opened”, as shown in FIGS.

FIG. 40B shows a state where the door is closed by a solid line, and shows a state where the door is slightly opened by a dotted line.
When the rotating body J rotates to close the door, the pulling spring V pulls the link AA to the door and the connecting shaft PP enters the “post-border area”, so the integrated rotating body J and link A slightly lift the door. Although it is rotated in the closing direction after opening, the pulling spring V remains stretched when opening the closed door, so that the connecting shaft PP does not enter the “post-border zone” and the door opens. .

Reversing the rotation direction of the door means stopping the rotation and decelerating close to a collision. Therefore, if the rotation of the drive unit is not rotated in the direction to open the door, the spring will not loosen if it simply moves with a spring. Since it continues to act, the door is accelerated without decelerating and is not temporarily stopped before the door is closed. When an inertial force acts on the rotation of the door, the force of the spring of the driving unit necessary for rotating the door becomes small, and a load is not applied to the spring. The spring that is not loaded is shrunk instantly and acts on the drive unit without loosening.
The force that the spring acts on the drive part becomes more than the force necessary to rotate the door, the door with inertial force will rotate more strongly, and it will accelerate further and a greater inertial force will work. . A spring force always acts on the door, and no matter how much the inertial force increases, the spring force exceeding that force acts on the door rotating by the inertial force in the same direction.

For this reason, even if an attempt is made to decelerate a large rotation of the drive unit to a small rotation of the door, the drive unit ends the rotation in an instant, and a deceleration due to the speed ratio cannot be expected. When the door is rotated by the “driving unit including the cam body and the cam wheel”, the time elapses and the door is slowly rotated.
In the embodiment of FIG. 13, a large rotation of the drive unit that rotates the door in the opening direction is applied to rotate the door so that the load is applied, and the drive unit does not end the rotation in an instant.

FIG. 40 (c) is similar to FIGS. 40 (a) and 40 (b) in that the connecting shaft C of the door D and the connecting shaft P of the rotating body J are connected by two links A and AA. Unlike 40 (a) and (b), the two links A and AA are not united, but the angle formed by the axis of the two links A and AA is “decreasing from fully open to closed. The door D is closed and rotated.
The door D10 immediately before closing, the rotating body J10, the link A10, the link AA10, the tension spring V, and the spring VV are shown by solid lines, and they are shown by dotted lines when fully opened and closed.
The link AA is urged by a spring VV so that its axis line is directed toward the door axis O in a “range from fully open to immediately before closing (A)”. For this reason, the force which rotates a door becomes small.
In the “range from just before closing to the closing time (i)”, the force of the pulling spring V that rotates the rotating body J exceeds the biasing force of the spring VV, and the axis of the link AA is parallel to the closed door D0. The link AA is rotated while being pulled in the direction toward the pivot axis O of the door.
As a result, the vehicle is temporarily stopped immediately before closing. At the time of sealing, the rotating body J, the link A, and the link AA are arranged on a substantially straight line, and their axis lines pass near the rotating body rotation axis Q. This causes a strong sealing force.

41 to 43 are operation explanation plan views for explaining the latch.
For example, if a magnetic catch is mounted instead of a latch, the spring force for sealing the door is not necessary, and the lightest feel is obtained when the door is opened. If the resistance of the latch is small at the time of sealing, the door can be rotated with a force slightly exceeding the maximum static friction force until it hits the door. In other words, the object of the present invention “slowly closing and always sealing” is made more possible.
41 to 43 provide a latch that has little resistance when the door is closed and prevents the door from reversing, and the spring force that presses the door when sealed is set to a force that keeps the door airtight. Not strong.

The spring force to rotate the door is small, and a large sealing force is applied to the closed door. The force required to open the door is the magnitude of the sealing force, and a door with a small sealing force is felt lightly when the door is opened.
A normal latch device is a door reverse rotation prevention device. When the latch abuts against the door frame W, the latch device moves parallel to the door surface and acts in a direction perpendicular to the moving direction. Although a large force is required for closing, the means for preventing the reverse rotation of the door is a structure that supports the force in the entire cross-sectional area, enters deep into the door frame, and has little backlash at the closed position.
41 to 43 show a latch male part attached to one of "the side surface of the door opposite to the door pivot" and "the side surface of the door frame facing it", a latch female part attached to the other, and the latch male part. A rotation support shaft having a vertical shaft core line; a claw rotatably supported by the rotation support shaft; a sliding surface provided in the latch female portion; and a recess provided in the sliding surface. A latch device that rotates around the rotation support shaft while the claw moves along the sliding surface to house the claw in the recess. Is. ,
The latch device shown in FIGS. 41 to 43 is rotated in the closed state, thereby bringing the moving direction and the direction in which the force acts closer to parallel. Thus, the sealing force is reduced by reducing the force for the latch to be recessed. In a normal latch, the force that prevents the door from reversing is a shearing force, and the portion that supports it is the side of the latch and is supported by a large contact portion. On the other hand, the latch device of the present invention is a force directed to the rotation axis in the latch, and the portion that supports this is supported by the outer edge of the latch, not the rotation shaft of the latch, and is supported by the large contact portion. The Further, even if the door frame does not enter deeply, it does not come out of the door frame, and the greater the force, the greater the braking force that is applied, and there is less backlash at the closed position.

The operation of the latch device shown in FIG. 41 will be described.
The embodiment of FIG. 41 provides a latch with low resistance when closed, and reduces the force when opening a closed door by reducing the sealing force. 41 is a horizontal sectional view (plan view) of a latch male part E attached to the side surface of the door D opposite to the pivot and a latch female part F facing it and attached to the side surface of the door frame.
The latch male part E includes a recess He that accommodates the claw Ge, and the rotation support shaft Ig is provided in the recess He. The claw Ge is rotatably supported on the rotation support shaft Ig, and the sliding surface Ke of the claw Ge includes a front end portion Pg and a front sliding surface Pk continuous thereto.
The latch female portion F is provided with a recess Hf that accommodates the claw Ge when the door is closed. The peripheral portion of the latch female portion F has an inlet portion Kf that moves along the front sliding surface Pk of the claw Ge, and a claw Ge that is continuous therewith. And a circumferential portion Rf that moves along the tip portion Pg. The shape of the circumferential portion Rf is centered on “the position of the rotation support shaft Ig0 of the claw Ge at the time of closing”, and “a distance rr between the rotation support shaft Ig and the tip portion Pg of the claw Ge” has a radius. It is a part.
In the conventional latch, there is a right-angle relationship between the storing direction and the direction of action of “force acting on the latch when the latch hits the metal fitting attached to the door frame”, which greatly resists rotation of the door when sealed. In the latch device shown in FIG. 41, since the claw Ge rotates and translates in the direction of the arrow E in the figure, there is little resistance acting on the rotation of the door when sealed.

41 (a), 41 (b), and 41 (c) show the states when closing, immediately before closing, and when opening. FIG. 41A is a state explanatory view when a force in the opening direction acts on the door at the closing time and the claw Ge receives a reaction force from the latch female portion F. FIG.
As shown in FIG. 41 (a), the line of action of “the force Fg for preventing reverse rotation of the door when closed” is a straight line passing through the rotation support shaft Ig and the tip portion Pg of the claw Ge. The force “Fg” is supported by the rotation spindle Ig. For this reason, it is necessary to increase the cross-sectional area of the rotation support shaft Ig. However, in the latch device shown in FIG. Mostly, it is supported not in the rotation support shaft Ig but in the range (a) of the circumferential portion Re.

The periphery of the claw Ge opposite to the tip portion Pg is provided with a circumferential portion Rg, and the circumferential portion Rg is a part of a circle having a radius r with the rotation support shaft Ig as a center. The portion Re is a part of a circle having a radius equal to or larger than the radius r with the rotation support shaft Ig as a center. “(A) range of the circumferential portion Re that accommodates the claw Ge” also functions as a “rotating bearing about the claw Ge” while being in contact with the “circumferential portion Rg of the claw Ge”. Instead, the reaction force Fg is supported. Therefore, the strength expected for the rotation support shaft Ig is reduced.
The spring U is attached to the concave portion He of the latch male part E, and urges the claw Ge around the rotation support shaft Ig in the direction of arrow A in the figure. As shown in FIG. 41 (c), the tip Pg of the claw Ge protrudes from the recess He in a state of being separated from the door frame W. Further, the tip portion Ree in the range (a) of the circumferential portion Re and its periphery serve as a hit for preventing the claw Ge from rotating in the direction of the arrow A in the figure. It does not prevent the claw Ge from rotating by providing a small bump contact.

As shown in FIG. 41 (c), when the door D moves in the direction of arrow E in the figure and moves to the state immediately before closing shown in FIG. 41 (b), the claw Ge slides. The surface Ke is in contact with the inlet Kf, the claw Ge rotates around the rotation support shaft Ig in the direction of the arrow B in the figure, and is received in the recess He provided in the latch male part E, and the claw Ge is received in the door. The When the door D further rotates, as shown in FIG. 41A, the claw tip Pg moves on the circumferential portion Rf of the recess Hf after passing over the entrance Kf of the latch female portion F.
When the shape of the circumferential portion Rf is a circle centered on the position of the rotation support shaft Ig0 of the claw Ge when closed, and the distance between the rotation support shaft Ig and the tip portion Pg of the claw Ge is a radius rr, When D abuts against the buffer portion Gz provided on the door stop Gw and the door is about to move in the direction of the arrow D in the figure, the rotation support shaft Ig is centered on the tip Pg of the claw Ge in the direction of the arrow C in the figure. Even when the claw Ge does not enter the recess Hf of the latch female portion F in an attempt to revolve, the door does not move in the direction of the arrow D.

As shown in FIG. 41 (a), when the gap between the latch male part E and the female part F is a length Lg, if the circumferential part Rf of the recess Hf is a circumference centered on the rotation support shaft Ig, When the gap is not Lg, the locus of the circular motion of the claw tip Pg does not follow the circumferential portion Rf.
If the gap is designed to be smaller than Lg, the claw tip Pg will not enter the recess Hf unless the door presses the buffer material Ge to contract. In this case, if the door is opened in the direction of the arrow D in the figure, the above-mentioned rotation support shaft Ig revolves and the reaction force acts on the tip portion Pg. The door contracts, and the repulsive force causes the door to be more firmly attached to the door frame.
In the above, when the gap is designed to be larger than Lg, the tip end portion Pg does not come into contact with the circumferential portion Rf but enters the depth of the recess Hf, but it becomes rattled when the door is sealed.

Arcs Rf0, Rf +, Rf− shown in FIG. 41 (c) are part of a circle having a radius rr, and the centers of the arcs Rf0, Rf +, Rf− are the position of the rotation support shaft Ig0, the position of Ig +, the position of Ig− To be part of a circle.
Assuming that the rotation support shaft Ig moves on the track Zig and passes the position of Ig0, when the circumferential portion Rf is an arc Rf0, Is always an acute angle when the circumferential portion Rf is an arc Rf +, and is always an obtuse angle when the circumferential portion Rf is an arc Rf−.
When the rotation support shaft Ig passes the position of Ig0 and approaches the buffer portion Gz, when the circumferential portion Rf is an arc Rf +, the door is more firmly attached to the door frame, and the circumferential portion Rf is an arc. When it is Rf-, it will rattle when sealed.
When the rotation support shaft Ig moves away from the buffer portion Gz, the tip portion Pg moves in the direction of being discharged from the recess Hf when the circumferential portion Rf is the arc Rf +, and the recess Hf when the circumferential portion Rf is the arc Rf−. Move in the direction to enter.
When the circumferential portion Rf is an arc Rf +, the more the door is closed, the tighter the seal is. However, when the force Fg in the opposite direction is applied, the door frame W comes off. However, if the intersection angle between the line of action of the force Fg and the arc Rf0 is not very acute, the tip Pg stops at the circumference Rf due to friction between the tip Pg and the circumference Rf, and the claw Ge is By rotating in the direction of the middle arrow A, the rotation support shaft Ig is moved from the position of Ig0 toward the position of Ig +, and the crossing angle turns into an obtuse angle. That is, it will not come off the door frame W.
For this reason, the circumferential portion Rf is designed so that the intersection angle between the line of action of the force Fg and the arc Rf0 is slightly acute.

The latch device of FIG. 42 includes a latch male part attached to one of “the side surface of the door opposite to the door pivot” and “the side surface of the door frame facing it”, a latch female part attached to the other, and the latch male part. A rotation support shaft whose axis core line provided in the portion is vertical, a claw rotatably supported by the rotation support shaft, and a sliding surface provided in the latch female portion,
The latch device is configured to rotate about the rotation support shaft while moving along the sliding surface, wherein the shape of the outer edge of the claw is the rotation shaft of the claw and the outer edge. The latch device is characterized by a vortex line in which the distance to the portion gradually increases or decreases.
FIG. 42 is a diagram in which the claw Ge of FIG. 41 is replaced with a claw Gb whose outer periphery is a spiral curve, and the outer edge is a spiral curve in which the distance from the rotation axis Ig to the outer edge gradually increases. As shown in FIG. 42A, the distance Lb between the “contact point b between the claw Gb and the latch female portion F” and the rotation axis Ig becomes larger as the claw Gb is rotated in the direction opposite to the arrow B in the figure. When the door is opened from the state shown in FIG. 42B, a force acts in the direction in which the gap expands Lg, and resistance is applied to prevent the opening.
When the door is closed, the claw Gb rotates in the direction of the arrow B in the figure, and the distance Lb between the “contact b between the claw Gb and the latch female portion F” and the rotating shaft Ig becomes small, and the resistance is hardly applied. You can hit the door to the door. In the latch device shown in FIG. 42, the latch female portion F shown in FIG.

FIG. 43 illustrates the interlocking between the latch portion of FIGS. 41 and 42 and the handle M, and the handle M is rotatably attached to a rotation shaft Im provided on the latch male portion E. FIG. The handle M has a rotary shaft Im as an intermediate portion, one of which is a grip portion M1, and the other is a contact portion M2.
As shown in FIG. 45 (a), when the door is sealed, the contact portion M2 comes into contact with the arm Em fixed to the rotation support shaft Ig of the claw Ge, and when the handle M is rotated in the direction of arrow A in the figure, the claw Ge As shown in FIG. 43 (b), the claw Ge is housed in the recess He, and the latch male part E and female part F can be separated to open the door. The direction in which the handle gripping part M1 is pushed is the direction indicated by the arrow C in the figure, and coincides with the door opening direction, so that the latch function is released at the same time the handle is pushed, and the door is opened at the same time.
FIG. 43 (c) shows a state just before the door closes, and the door moves in the direction of arrow D in the figure and the claw Ge rotates in the direction of the night mark in the figure, but the handle is not interlocked with this. The abutting portion M2 of the handle is pressed against Gm by the pressing spring Um and does not contact the arm Em.

The deceleration at the time of sealing will be described.
As shown in FIG. 1, the rotational force acting on the door, which is a rotational force that starts moving the stationary door, is slightly larger than the maximum static frictional force and starts to move. Even if the frictional force acting on the door is reduced, it is subject to air resistance, so “slightly greater than the maximum static frictional force” approximates the balance between the air resistance and the rotational resistance of the pivot of the door. Without moving at a constant speed. However, as long as the rotational force acting on the door continues to act even slightly, the rotational speed of the door is accelerated, so that means for decelerating the rotation of the door is required.
When the closing of the door approximates the constant velocity motion described above, the closing speed of the door is too slow, and the door is desired to close quickly. In this case, the rotational force acting on the door, that is, “slightly larger” than “the force that is slightly larger than the maximum static frictional force” is a force that causes the door to close quickly by approximating the constant velocity motion described above. However, in any case, as long as the force continues to act, the rotation speed of the door is accelerated, so a means for decelerating the rotation of the door is required.

Technology that allows the door to rotate with a weak rotational force in the “range from fully open to just before closing (A)”, and tightly seals the door with a weak rotational force in the “range from just before closing to the time of closing (Yes)” Is established as described in the embodiment of FIGS. 1 to 40, and after the door rotates with a weak rotational force, when a larger sealing force is applied to the door, the rotational speed of the door is further accelerated and the sealing is performed. It has been described in the description of the embodiment in FIG.
The force required to dent the latch at the time of sealing is large, and the static load when denting the latch of the stationary door is large, and the force of the strong spring needs to act on the door. However, when dynamic inertia is attached, or when an impact load is applied when the door collides with the door stop at the time of sealing, the force of the spring does not need to be applied at all.

In most cases where the latch is recessed, the rotation speed of the door is not zero, and the door itself has sufficient sealing force necessary to dent the latch, and the spring force also dents the latch. Moreover, it is extra for sealing the door, and further accelerates the rotational speed of the door to be sealed, and a large impact sound at the time of sealing is unavoidable. Therefore, the door cannot be closed quietly unless the rotation speed of the door immediately before the latching in which the latch is recessed is made as close to zero as possible and the sealing force is made as small as possible.
Even if the spring force is set to force the depression of the latch, if there is any inertial force attached to the door at the time of sealing, the spring force is completely unnecessary, and only the impact sound is removed when the inertial force is completely removed. Can be avoided. The impact sound is inevitable unless a small rotation of the door during sealing takes a long time. Since the rotation of the sealing device of the present invention is several times the “door rotation at the time of sealing”, it is easier to decelerate the rotation of the sealing device than to directly decelerate the rotation of the door. Further, in the present invention, the acceleration of the door is significant only at the time of sealing. At the beginning of the range until the closing time (i), a means for eliminating the inertial force or a means for reducing the sealing force is required.
In the latter case, the “range from just before closing until closing” (i) where the sealing device operates is divided into “range (good) where the speed reducer operates” and “range (i) where the sealing device operates”. It is done.

The sealing device has a rotating portion. In many cases of the sealing device of the present invention except for the embodiment of FIG. 20, the rotating portion of the sealing device is a link A or a rotating body J, and the link A or the rotating body. J rotates about a rotation support shaft provided on the door D or the door frame W. In the “range in which the speed reducer operates (good)”, the rotating portion of the sealing device rotates, and the rotation support shaft of the rotating portion of the sealing device approaches the door D or the door frame W.
If the spring force does not need to rotate the door D immediately before the door is sealed, the link A will rotate in an instant in a no-load state, and the door will be sealed without decelerating, but this is not done. The means for this is the door within the “range where the speed reducer operates (good)”, even if the link A or the rotating body J rotates or the rotating support shaft does not approach or approaches the door D or the door frame W. It is made to prevent it from rotating until it contacts a door stop.
For example, by setting the portion K1 of the sliding surface K where the wheel B moves in the “range where the speed reducer operates (good)” as “an arc centered on the position just before the rotation support shaft closes”, the wheel B Even if it moves on the arc K1, the rotation support shaft does not move from the position just before the closing, and the door is temporarily stopped before the closing.
For example, as shown in FIG. 44 (a), there is a link A that rotates about a connecting shaft C provided on the door D and a sliding body K that attaches to the door frame W, and the connecting shaft C just before the sliding body K is sealed. Assuming that the circumference is centered on the position of, it is attached to the rotary spindle Ib provided in the middle part of the link A “just before the door is sealed when the wheel B moves along the sliding surface K. Pause at the position.

The speed reducer operating in the range (good) will be described with reference to FIG.
44 is a plan view for explaining the means for decelerating the door in the range (good) and the means for sealing the door in the range (color). FIG. 44 shows the door having the structure shown in FIG. The illustration of the spring is omitted in 44 (a) and 44 (b).
The sliding surface K of the components constituting the sealing device is attached to the door frame W, and the wheel B, which is another component of the sealing device, is attached to the “door surface opposite to the door surface contacting the door stop”. It is attached to the middle part. The wheel B revolves around the connecting shaft C and moves along the sliding surface K. The contact point b is a contact point between the sliding surface K and the wheel B, and the sliding surface K is an arc whose radius is the distance between the contact point b and the connecting shaft C.
44A is a part of a circle centered at points C20 and C10 in the figure, respectively, and the points C20 and C10 in the figure are in a stationary state with each centered. When the wheel B revolves, the locus of the contact point b becomes K20 and K10.
When the wheel B revolves around the connection axis C20 and moves along the sliding surface K20, the rotation of the door D is stopped. Further, when revolving around the connecting shaft C10 and moving along the sliding surface K10, the rotation of the door D is stopped.

The operation will be described with reference to FIG.
As the door D rotates in the direction of arrow B in the figure, the connecting shaft C moves “on the circular track Roc centered on the door pivot O”. Assuming that the door D is temporarily stopped at the position of D20 and the link A rotates about the connection axis C20, the rotation support shaft Ib indicates “on the circular orbit Rc20 centering on the connection axis C20” as shown by the arrow A in FIG. Move in 20 directions. On the contrary, when the rotation support shaft Ib moves on the circular orbit Rc20 centering on the connection axis C20 in the direction of arrow A20 in the figure, the door D temporarily stops at the position D20. Similarly, when the link A rotates about the connection axis C10, the rotation support shaft Ib moves on the circular orbit Rc10 centering on the connection axis C10 in the direction of arrow A10 in the figure, and the door D is positioned at D10. Pause at.
In each case, if the sliding surfaces along which the wheel B moves are K20 and K10, the sliding surfaces K20 and K10 are arcs centered on C20 and C10, respectively, and C20 and C10 are the pivot axis O of the door. Since it revolves around the center, the sliding surfaces K20 and K10 revolve around the pivot axis O of the door.

As shown in FIG. 44 (b), the sliding body KK has the sliding surface K and is rotatably supported around the pivot axis O of the door. The wheel B is kept in contact with the sliding surface K. Before the link A rotates about the connecting shaft C at an arbitrary position, the wheel B is in a linear portion of the sliding surface of the sliding body KK, and after the rotation, , In the arc part.
When the link A rotates about an arbitrary position of the connecting shaft C, the door D stops when the wheel B continues moving in contact with the sliding surface K assuming that the sliding body KK is stationary.
The sliding body KK shown in FIG. 44 (b) is urged by the pressing spring U, abuts against the Gkk, and is prevented from rotating in the direction opposite to the arrow C in the figure. The sliding surface of the sliding body KK20 that is in contact with Gkk as shown by the dotted line is the sliding surface K20, and the sliding surface of the sliding body KK10 that is illustrated by the solid line is the sliding surface K10. The sliding body KK rotates and swings slightly between the sliding body KK10 illustrated by a dotted line and the sliding body KK10 illustrated by a solid line with the pivot O of the door as an axis.
In FIG. 44 (b), if the wheel B collides with the sliding body KK20 when the door D reaches the position D20 after moving "on the circular orbit Rob centered on the door pivot O", the collision occurs. The shock is reduced by the compression spring U being contracted and the sliding body KK rotating from the position KK20 to the position KK10. While the sliding body KK rotates, the wheel B moves along the sliding surface K, and the door D is temporarily stopped at the position D10.

The push spring U is for keeping the wheel B and the sliding surface K in contact with each other, and there is no force to rotate the door D in the direction of pushing back and opening the center of the revolution of the wheel B and the sliding surface K. Since it approximates the state where the center of the circle coincides, it does not resist the rotation of the link A. However, in the door D where dynamic inertia is attached, the wheel B moves while pressing the sliding surface K, so that rolling friction occurs on the wheel B, and in FIG. 44 (b), the door D moves from the position D20 to the position D10. There is no longer a situation in which the link A rotates instantaneously in a no-load state due to the passage of time.

FIG. 44 (c) is a closed state diagram showing the structure of the apparatus of FIG. 4, and the position of the rotary shaft of the sliding body KK is set to a position Okk away from the pivot axis O of the door.
K10 indicated by a dotted line is a circumference centered on the position C10 of the connecting shaft C of the door immediately before sealing, and the sliding body K whose circumference slide surface K centering on C10 rotates around Okk is the sliding body KK. is there. Since the rotation angle of the link A is small, the center of the circle of the sliding surface K indicated by the solid line is the position of CC20 slightly separated from the position of C20, and the sliding surface K shown in FIG. ) To approximate the sliding surface K20.
When the wheel B moves along the sliding surface K10 and enters the depression KKK, the sliding body KK rotates in the direction opposite to the arrow C in the figure by the pressing spring U, and comes into contact with Gkk and stops. The wheel B is restrained by the projection KKK20 in the stationary recess KKK, and exerts a sealing force on the door D in the direction of arrow B in the figure. Since the sliding body KK is prevented from rotating in the direction opposite to the arrow C in the figure by the contact Gkk, the position of the protrusion KKK20 is a position where it does not move and supports the reaction force of the sealing force.

The sliding body KK is never sealed while the wheel B is moving on the sliding surface K even if the position of the connecting shaft C of the door immediately before the sealing stays in the same position or moves. There is no such thing.
The shape of the sliding surface K of the sliding body KK can be the position of the connecting axis C, whether it is a circumference K10 centered on the position C10 of the connecting axis C of the door immediately before sealing or a circumference close to it. It may be a spiral curve that gradually decreases or increases the distance to C10.
While the wheel B is moving on the arc of the sliding surface K, it is desirable that the latch is in contact with the door frame W. Even when the door is stopped, the link A continues to rotate and the operation of the closing device stops. do not do.
If the latch is in contact with the door frame W before the wheel B moves on the arc of the sliding surface K, the rotation of the link A stops when the door stops.

Since the link A rotates without rotating the door, the door will not remain stopped even if there is no force to seal the door when the link A starts to rotate. That is, the force for sealing the door does not exist before the latch contacts the door frame W, and the latch contacts the door frame W after the door is decelerated and stopped. After the latch comes into contact with the door frame W, a force for sealing the door is generated, and the door is gently sealed. When the wheel B moves away from the end of the arc portion of the sliding surface K and enters the recess KKK, the “force for pressing the door” is sufficient for the latch to start to be recessed, and the latch starts to be recessed. Since resistance is added to the rotation of the door when the latch is recessed, the door is decelerated when sealed.
44 "apparatus that prevents sealing and decelerates just before closing" in FIG. 44 applies a resistance in the opposite direction to "the force that rotates the door in the closing direction" as in a normal speed reducing device, and "rotates the door in the closing direction. Since the “force” is not reduced, the “force for rotating the door in the closing direction” is not further increased to counter the “large force in the opposite direction” as in a normal reduction gear.
44, the moving wheel B is attached to the door, and the stationary sliding surface K is attached to the door frame W. The wheel B is inserted between the door D and the sliding surface K, This is a mechanism that increases the distance between the sliding surface K and presses the door D against the door, and is a sealing mechanism that enables the door to be tightly sealed with a small force by a so-called wedge effect. The direction of movement of the wheel B at the time of sealing is substantially parallel to the closed door surface D0, and the direction of the sealing force acting on the door is substantially perpendicular to the closed door surface D0.

As shown in FIG. 44 (c), the link A starts to rotate only after the “connection shaft C revolving around the pivot axis O of the door” crosses the axial line Zv of the tension spring V. When the speed of the door is accelerated immediately before closing, the wheel B moves along the arc portion of the sliding surface while compressing the push spring U when the link A rotates, thereby resisting the rotation of the link A. As it is added, it is sealed while decelerating. When the speed of the door is not accelerated immediately before closing, the wheel B moves along the arc portion of the sliding surface without compressing the compression spring U. Alternatively, the link A rotates away from the arc portion of the sliding surface, and the link A rotates in an instant in an unloaded state. That is, the greater the inertial force attached to the door, the slower the movement of the wheel B and the greater the deceleration effect.
Further, when the inertial force attached to the door is increased, the wheel B compresses the compression spring U and stops at the entrance or midway of the arc portion of the sliding surface. When the inertial force attached to the door eventually disappears, the push spring U is restored and rotated in the direction to open the door.

As shown in FIG. 44 (c), when the connecting shaft C is movably attached to the door D via the rotating body Jc, the rotating body Jc rotates around the rotating shaft Ij in the direction indicated by the arrow E in the figure. The distance “Lc between the connecting shaft C and the door surface” increases, and the restoring force of the push spring U is not transmitted to the door, and the door does not rotate in the opening direction. In FIG. 44 (c), the inertial force that subsequently attaches to the door disappears, the wheel B reaches a position where it presses the projection KKK20, the end on the connecting shaft C side of the rotating body Jc presses the door surface, Shown in a sealed state.
Further, when the inertial force attached to the door is increased, the rotating body Jc rotates around the rotation axis Ij in the direction indicated by the arrow E in the figure, When hitting the door surface, the distance Lc is expanded to the maximum, and at this time, the push spring U is also contracted to the maximum, and the wheel B stops moving. When the inertial force that attaches to the door eventually disappears, the push spring U is restored and rotates in the direction to open the door, and then the wheel B starts to move and reaches the position where the protrusion KKK20 is pressed, and the door is sealed. To do.
In this way, when the door closes due to the strong wind, the door opens once before closing and then closes. In other words, a finger-tight accident is prevented.

The spring mechanism used in FIG. 44 is the spring mechanism of FIGS. 3 and 4, and is closed from “the rotation angle Θd of the door when the link A starts rotating away from the contact” when the door is closed. When the door is opened, “the rotation angle Θd of the door when the link A away from the contact comes into contact again” becomes large.
In the spring mechanism shown in FIGS. 3 and 4, the link A does not rotate in the opposite direction to the rotation at the closing time until the connecting shaft C crosses the axis of the tension spring V when the closed door is opened. As shown in FIG. 44 (c), the wheel B moves along the sliding surface K5 facing the depression KKK, and the link A rotates in the direction opposite to the rotation at the closing time. As a result, the axis of the tension spring V is pulled toward the connection shaft, and the axis of the tension spring V crosses the connection axis C. Can be small.

The speed reducer operating in the range (good) will be described with reference to FIG.
FIG. 45 is a plan view for explaining the means for decelerating the door in the range (good) and the means for sealing the door in the range (color). FIG. 45 shows the door having the structure shown in FIG.
The link A of the “rotating part of the sealing device” rotates about the rotation axis Sw fixed to the door frame W, and the sliding surface K attached to the link A is an arc centered on the rotation axis Sw, and is attached to the door. It is the Example in case the wheel B with which it mounts | attaches to "the door surface of the side contact | abutted with a door stop". Even if the link A rotates, the wheel B that moves along the sliding surface K maintains a certain distance from the rotation axis Sw, and the rotation of the door D stops just before closing.

The operation will be described with reference to FIG.
The means for decelerating at the end of the “range (A)” is along the sliding surfaces K20 and K10 provided on the “link A that is rotatably supported around the rotation axis Sw provided on the door frame W”. When the wheel B moves from the sliding surface K20 along the sliding surface K10 as shown in FIG. 45 (a), the speed is reduced by changing the traveling direction to a substantially right angle. The wheel B that collides with the sliding surface K10 is movable, and the link A rotates by absorbing the impact that occurs when the wheel B collides with the sliding surface K10 due to the expansion and contraction of the spring. When doing so, the wheel B is not pulled away from the sliding surface K10.

A corner portion connecting the sliding surface K20 to the sliding surface K10 is a portion that smoothly changes the traveling direction of the wheel B, and the wheel B changes the traveling direction to a substantially right angle while the door D rotates. It is a part to do. When the inertial force attached to the door is large and the wheel B reaches the corner, the door bounces back in the opening direction. Will be.

Until the axial center line Zv of the pulling spring V crosses the rotation axis Sw when the door is closed and rotated, the door abuts against Ga, and the rotation of the link A in the direction opposite to the arrow A in the figure is prevented. As shown in FIG. 45 (a), when the wheel BB attached to the tip of the link A comes into contact with the door surface and moves along it, the degree to which the length of the tension spring V decreases is reduced. The door slows down. The means by which the fulcrum of the tip end of the link A of the tension spring V is moved by the door is also a means for decelerating at the end of the “range (A)”.
As shown in FIG. 45 (b), the means for decelerating the door in the range (good) is such that the shape of the outer edge of the sliding surface K10 is a circumference centered on the rotation axis Sw or a spiral curve similar thereto. When the wheel B moves along the sliding surface K10, the door D does not hit the door and is temporarily stopped.

When the axial center line Zv of the tension spring V crosses the rotation axis Sw as shown in FIG. 45 (b), the door moves away from Ga and the link A rotates in the direction of arrow A in the figure. The rotation of the link A does not need to be accompanied by the rotation of the door, and the rotation angle of the link A is not limited.
As shown in FIG. 45 (c), when the wheel B moves along the sliding surface K10 and then enters the recess KKK, the wheel B is restrained by the sliding surface K5 in the recess KKK, and the arrow D in FIG. The direction A sealing force is applied, and the link A rotates greatly and stops.

As shown in FIG. 45 (c), the means for sealing the door in the range (color) includes the sliding surface K5 provided on the link A and the pivot axis O of the door attached to the “door surface in contact with the door stop”. A wheel B that revolves around the center and includes a wheel B that moves along the sliding surface K5, and the sliding surface K is inserted between the door D and the wheel B and attached to the door. The sliding mechanism K5 is drawn to the rotating shaft Sw of the sliding surface K5 while the sliding surface K5 rotates. It is a sealing mechanism that enables the door to be tightly sealed with a small force by the so-called wedge effect. The direction of movement of the wheel B at the time of sealing is substantially parallel to the closed door surface D0, and the direction of the sealing force acting on the door is substantially perpendicular to the closed door surface D0.

When the closed door is opened, the link A rotates as the wheel B moves along the sliding surface K5, the axial center line Zv of the tension spring V crosses the rotation axis Sw, and the link A is shown in FIG. As shown in a), the state returns to the state of contact with the contact Ga.
When there is no sliding surface K5, the link A rotates until the fulcrum C0 on the door side of the tension spring V revolves around the pivot axis O of the door, and the axis Zv of the tension spring V crosses the rotation axis Sw. The link A rotates momentarily and collides with Ga at the same time as the axis Zv of the tension spring V crosses the rotation axis Sw.

The operation will be described with reference to FIG.
46 has a structure in which the wheel B revolves around the rotating body rotation axis Q attached to the door frame W and the sliding surface K is attached to the door surface as shown in FIG. The sealing mechanism is inserted between the door D and the rotating body rotation axis Q, and increases the distance between the door D and the rotating body rotation axis Q to press the door D against the door.
The rotating body rotating shaft Q revolves around the rotating shaft QQ of the rotating body A to increase the fully open angle of the door D as shown in FIG. The sealing mechanism of FIG. 46 does not leave the wheel B from the sliding surface K in the entire process from fully open to closed as shown in FIG. In addition to this function, a function of rotating the door in the “range from fully open to immediately before closing (A)” is added.

The sliding body KK having the sliding surface K is pivotally supported around the connecting shaft C of the door so as to be able to rotate the load, and is not fixed to the door D as shown in FIG.
The closer to the door surface D0 the moving direction of the wheel B is when closed, the closer to the closed door surface D0 the direction of the sealing force acting on the door is, the stronger the "force to seal the door" is. However, when the closed door is opened, the wheel B hardly starts moving on the sliding surface K, and resistance is applied when the closed door is opened.
The sealing device of FIG. 46 is such that when the closed door is opened, the sliding surface K rotates about the connecting shaft C, and the sliding surface K that is substantially parallel to the door surface D0 has a gradient. The wheel B is easy to start moving on the sliding surface K.

46 (a) to 46 (b), while the rotating body J rotates around the rotating body rotation axis Q, the rotating body A rotates around the rotating axis QQ and the door D rotates. It keeps in contact with the contact Ga and stops still.
46 (a) to 46 (b), the sliding body KK comes into contact with Gk and is fixed to the door D. However, as shown in FIGS. 46 (b) to 46 (c), the tip of the sliding body KK. KKa comes into contact with the door frame W, and the sliding body KK is separated from Gk and rotates about the connecting shaft C. The leading end KKa moves along the door frame W toward the door pivot O.
The force with which the wheel B presses the sliding surface K is supported at two locations of the connecting shaft C and the door frame W, the spring force is dispersed, and a part of the spring force becomes a force for rotating the door. At the end of the “range (A)” shown in FIGS. 46B to 46C, the wheel B moves on the sliding surface K in a direction away from the connection axis C, so that the force for rotating the door is further reduced. The door closing speed is reduced.

46 (c) to 46 (d), the wheel B moves on the sliding surface K in a direction approaching the connection axis C, the tip KKa is separated from the door frame W, and the sliding body KK is The connecting shaft C rotates about the shaft. During this process, the outer edge KKb of the sliding body KK moves along the door frame W. Since the outer edge portion KKb is a part of a circle centering on the connection axis C, the distance between the door and the door frame is kept constant, and the door is prevented from being sealed.
In the range (color) shown in FIG. 46 (d), when the sliding body KK further rotates around the connecting shaft C, the outer edge KKc of the sliding body KK contacts the door frame W, and the space between the door and the door frame is reduced. Shorten the distance and close the door. During the rotation of the sliding body KK about the connecting shaft C, the force with which the wheel B presses the sliding surface K0 acts in the direction perpendicular to the sliding surface K0, and the line of action sometimes passes through the rotational axis QQ. If the latch is recessed at this time, as shown in FIG. 46 (d), the sliding body KK closes at the end of the rotation about the connecting shaft C, and the door is closed. Strong sealing force is not acting.

44 is a circle centered on the position of the connecting axis C just before the door is sealed, and the wheel B attached to the door moves along the sliding surface K attached to the door frame W. FIG. In FIG. 46, the door is hermetically sealed by moving a sliding surface of a circle centering on the rotation axis Sw provided on the door frame W along the wheel B attached to the door at a position immediately before the door is sealed. When the sliding surface K of the circle centered on the connection axis C moves along the door frame W at the immediately preceding position, the distance between the door and the door frame is kept constant, and the sealing device rotates. The door is prevented from being sealed while it is still.

47 and 48, when the damper described later in FIG. 44 to 46 is attached to the sealing device illustrated in FIGS. 44 to 46, the time during which the sealing device rotates is increased, and the time from just before the door is sealed until the door is sealed become longer.
When the damper is not attached, the state in which the wheel B moves along the sliding surface of the circle or the state in which the sliding surface K of the circle moves along the door frame W differs depending on the magnitude of the inertial force attached to the door. . When the inertial force attached to the door is small, the above movement ends instantaneously and does not decelerate in the range (good). Depending on the magnitude of the inertial force attached to the door, a large frictional resistance acts on the movement and decelerates in the range (good). Since K moves away from the door frame W, the above movement is completed in an instant and there is no effect of the deceleration function.
The “rotating means in the range of (ii)” of the present invention is a sealing mechanism that generates a large force when the door is stationary and operates without rotating the door. finish. If the operation of the apparatus takes time and the sealing force is not impaired without stopping the operation, the door is gently sealed.
The damper described later with reference to FIGS. 47 and 48 is a “door having a one-way operation damper that operates in the“ rotating means in the range of (i) ”.

Even if the "sealing device is also a rotating part" rotates greatly at the time of sealing, the rotation of the door is slight, and the spring does not need to rotate the door. Even if the speed reducer operates before the door is sealed, the door is accelerated at the time of sealing. If the force of the spring is not set to the minimum necessary to barely dent the latch, a severe impact sound will be generated.
In order not to generate a large impact sound at the time of sealing, the “time from the start of the latch to the end of the latch” is lengthened so that a long time is required for the sealing operation.
47 and 48, the “elapsed time from the start of the latch to the end of the recess” is extended by the damper.

47 and 48, the structure of the damper is shown in cross section.
47 and 48, the opening at one end of the cylinder Sl is blocked by a sealing lid Sla, and the opening at the other end is a lid having a through hole through which the shaft Pss passes in the center. Slb allows air in and out. The cylinder Sl is separated by a piston Ps into a sealed chamber Sli on the sealed lid side and an external air pressure chamber Slo on the lid side having a through hole, and the sealed chamber Sli is pressurized or depressurized by the reciprocating motion of the piston.
The piston Ps has a through hole in the center, and the shaft Pss passes through the through hole. The piston Ps is mounted so as to be able to reciprocate along the shaft Pss, and reciprocates between Pa per tip provided at the tip of the shaft and Pb per intermediate portion provided at a position more than the piston thickness from the tip. it can.

In the case of FIG. 47, Pa per tip is a valve that shuts off the intake air to the sealed chamber Pli. When the shaft Pss is pulled out from the cylinder Sl, the piston Ps moves toward the Pa per tip along the shaft Pss. It moves in close contact with Pa per tip, and shuts off air from entering and exiting the sealed chamber Sli and depressurizes the sealed chamber Sli.
In the case of FIG. 48, Pb per intermediate portion is a valve that shuts off the exhaust from the sealed chamber Sli, and when the shaft Pss is pushed into the cylinder Sl, the piston Ps moves toward the Pb per intermediate portion along the shaft Pss. It moves and comes into close contact with Pb per intermediate part, blocks air from entering and exiting the sealed chamber Sli and pressurizes the sealed chamber Sli.

In the case of FIG. 47, the inclined surface of the conical hole formed on the piston Ps and the conical inclined surface of Pa per tip are kept in airtightness, and the piston Ps and the intermediate portion Pb The piston Ps does not block air in and out even if it is in close contact. Therefore, there is no resistance when the shaft Pss is pushed into the cylinder Sl.
In the case of FIG. 48, the piston Ps and the intermediate portion Pb are kept airtight by interposing a packing Pc of rubber or the like between them, and the piston Ps and the tip portion Pa are in contact with each other even if they are in close contact with each other. Do not block access. Therefore, there is no resistance when the shaft Pss is pulled out from the cylinder Sl.
The cross-sectional shapes of the cylinder Sl and the piston Ps are not exactly the same, and it is designed so that the gas in the cylinder Sl slightly leaks from the piston Ps side, or in the case of FIG. In the case of 48, when the sealed chamber Sli is pressurized, the movement of the piston Ps takes time, and the rotation of the door D becomes slow.

The cylinder Sl is rotatably supported around a rotation support shaft Slw provided on the door frame W, and an end portion of the shaft Pss is connected to a rotation support shaft Pssj provided in an intermediate portion of the rotating body J. The amount of the shaft Pss that enters and exits the cylinder Sl is small in the “range (A)” and becomes large at the time of sealing, and the buffering effect of the damper is greatly exerted at the time of sealing in the “range (Iro)”. This reduces the impact sound generated by the large sealing force during sealing.

The operation will be described with reference to FIGS.
47. FIG. 48 shows that in the range (good), the wheel BB enters the sliding surface KK in a direction perpendicular to the sliding surface KK and moves on the sliding surface KK in the parallel direction, thereby decelerating the rotation of the rotating body J and decelerating the door. 47 is a plan view for explaining the means and the means for sealing the door while being buffered by the damper in the range (color). FIG. 47 shows the door having the structure shown in FIG. A turnbuckle TB is attached to the tension spring V attached to the shaft Sj and the support shaft Sw fixed to the door frame W, and the position where the support shaft Sw is fixed rotates around the support shaft Sww fixed to the door frame W. Adjust with expansion joint TA. The rotation of the link A is limited by the hit Gd and the hit Gj.
The structure of the closing device of FIG. 48 is similar to the structure of the closing device shown in FIG. 13 in that the connection shaft C of the door D and the connection shaft P of the tip of the rotating body J are connected to two links A and AA. The illustration of the mechanism of the spring that rotates the rotating body J of the closing device of FIG. 48 is omitted.
As shown in FIG. 48 (b), the direction in which the link AA faces changes from a direction perpendicular to the door surface to a parallel direction, whereby the rotational speed of the door is reduced. In the embodiment shown in FIG. 13, rotating in the direction in which the door opens just before closing means that the rotation speed becomes zero at the moment when the rotation direction changes, and a collision occurs immediately before closing, so FIG. 48 shows in the embodiment in FIG. As shown in FIG. 13, the rotating body J is not bent into a “shape” as in the embodiment.

Arm Ab in FIG. 47 FIG. 48 is rotatably supported around a rotation support shaft Ia provided at an intermediate portion of the link A, the wheels BB is mounted to the rotating shaft Ib provided at the tip portion of the arm Ab . The arm Ab is biased by the pulling spring VV, and the approach angle of the arm Ab to the sliding surface KK is adjusted by the hitting Gab.

47 (a) to 47 (b), as shown in FIGS. 48 (a) to 48 (b), the wheel BB enters the sliding surface KK in a direction perpendicular to each other, and FIGS. 47 (b) to 47 (c) and FIG. 48 (b). ) To (c), it moves on the sliding surface KK in the parallel direction, the tension spring VV is extended and the force is stored, and the rotation of the rotating body J is decelerated. Initially, when the wheel BB enters the sliding surface KK in the direction perpendicular to the tension spring VV, a large rotational moment acts on the arm Ab, but the arm Ab further rotates and the tension spring VV extends. However, the rotational moment acting on the arm Ab is small and does not resist the subsequent rotation of the link A.

47. In FIG. 48, the means for decelerating in the “range (good)” is a means for reducing the force for closing the door by applying a force in the direction opposite to the direction of the closing force. ) ”, The“ force acting in the direction opposite to the direction of the closing force ”changes in the direction of the force acting in the“ range ”, and acts in the closing direction to add a sealing force. As shown in FIG. 47 (c), the wheel BB moves on the sliding surface KK and approaches the rotation axis C of the link A so that the door is not sealed. As shown in FIGS. 47C to 47D, when the link A starts to rotate, the wheel BB moves away from the rotation axis C of the link A while moving on the sliding surface KK, and the force stored in the tension spring VV is Works in the direction of sealing the door.
As shown in FIG. 48 (a), the two links A and AA are kept in a straight line in the “range from fully open to just before closing (A)”, and the rotating body J and the link A are interposed between them. The pressing spring U is not pressed. Further, in the process between FIG. 48A and FIG. 48B, the rotating body J and the link A press the pressing spring U, so that the rotational speed of the door is reduced. As shown in FIG. 48 (c), the force stored in the push spring U is released and acts in the direction of sealing the door.

The “means for decelerating in the range (good)” described in FIGS. 44 to 48 resists the door to be closed with a certain size regardless of the closing speed of the door immediately before closing.
In a door that rotates with the force of a weak spring, when the hand is released from a slightly opened position, the closing speed of the door immediately before sealing is small, and the dynamic inertia force that attaches to a heavy door is small. On the other hand, when the hand is released from the fully open position, the closing speed of the door immediately before sealing is large, and the dynamic inertia force that attaches to the heavy door is also large.
44 to 48, the speed reducer that is effective when the hand is released from the slightly opened position may not be effective at all when the hand is released from the fully opened position. Yes, and a reduction gear that is effective when the hand is released from the fully opened position is too effective when the hand is released from the slightly opened position, resulting in stopping the rotation of the door. .
As the dynamic inertia force attached to the door increases immediately before sealing, the deceleration effect increases, and as the dynamic inertia force decreases, the deceleration effect decreases. It is desirable to use a speed reducer in which the attached dynamic inertial force acts as a force to decelerate the door.

The “decelerator that works as a force that the dynamic inertia force decelerates the door” in FIG. 49 will be described.
49, as in the embodiment of FIGS. 21 and 22, the wheel Bb moves while simultaneously contacting the sliding surface Kd attached to the door D and the sliding surface Kb attached to the door frame W to seal the door by the wedge effect. This is a structure that adds a function of “the dynamic inertia force attached to the door acts as a force to decelerate the door”.
46, the rotating body rotation axis Q revolves around the rotation axis QQ of the rotating body A, and the wheel B revolves around the rotating body rotation axis Q. The wheel B does not leave the sliding surface K in the entire process from full opening to closing as in the embodiment.

The long hole Hw is attached to the door frame W or its peripheral wall surface, and the sliding surface Kw is an inner edge portion of the long hole Hw on the side close to the door frame W. The sliding body KK is rotatably supported around a connection shaft C provided on the door D, and the sliding surface Kd is an inner edge portion of the sliding body KK on the side close to the door frame W of the long hole Hd. The illustrated wheel B is one wheel that moves along two sliding surfaces Kw and Kd at the same time, or two wheels that move along each of the two sliding surfaces Kw and Kd and share a rotation axis. It is.

In the latter case, the wheel Bb and the wheel Bd are fixed to the rotation axis Ib of the wheel illustrated in FIG. 22, and the two wheels Bb and Bd move simultaneously along the two sliding surfaces Kw and Kd. In this case, since the rotation directions of the respective wheels are opposite to each other, a strong brake is applied to the movement of the wheel rotation axis Ib. When the door is decelerated just before sealing and the “dynamic inertia force attached to the door” disappears, the two wheels Bb and Bd do not move along the two sliding surfaces Kw and Kd at the same time. The brake is not applied to the movement of the axis Ib.
When the wheel Bb and the wheel Bd are rotatably supported on the wheel rotation axis Ib illustrated in FIG. 22, the wheels rotate in opposite directions to each other, so that a powerful brake is applied to the movement of the wheel rotation axis Ib. Although not required, the effect of “the dynamic inertia force attached to the door acts as a force to decelerate the door” is recognized.

The operation will be described with reference to FIG.
The wheel B moves in the direction away from the door pivot O along the sliding surface Kw in the process from full opening to closing, and the point of action of the force for sealing the door is located away from the door pivot O. At the same time, the wheel B moves toward the connection axis C along the sliding surface Kd.
As shown in FIG. 49 (a), the sliding body KK is in contact with Gk in the process of being fully opened and closed, and rotation around the connecting shaft C in the direction indicated by the arrow C in FIG. The tip KKa is not in contact with the door frame W.
In the closing process shown in FIGS. 49B to 49D, the tip KKa of the sliding body KK contacts the door frame W and moves in the direction of the pivot axis O of the door. The wheel B moves toward the connection axis C along the sliding surface Kd, but the force with which the wheel B presses the sliding surface Kd is supported by the connection shaft C and the tip KKa of the sliding body KK. Is smaller the further away from the connection axis C, the smaller the force to rotate the door. 49D, when the wheel B is closed, the wheel B is in a position close to the connecting shaft C, and most of the force with which the wheel B presses the sliding surface Kd is supported by the connecting shaft C, thereby strengthening the door. Seal.
The force for rotating the door is large when the door starts to move when the door is fully open, decreases after the door starts to move, and increases again when the door is sealed.

When the inertial force attached to the door is large immediately before closing, the wheel B contacts the side Kw of the long hole Hw near the door frame W and the sliding surface Kdd of the long hole Hd on the side far from the door frame W. When the wheel B is considered as the two wheels Bb and Bd illustrated in FIG. 22, the wheel B moves along the two sliding surfaces Kw and Kdd at the same time, and the rotation directions of the respective wheels are opposite to each other. Even when the inertial force is small, the wheel B contacts the sliding surface Kd on the side close to the door frame W of the long hole Hd and the sliding surface Kww on the side far from the door frame W of the long hole Hw. In this case, the rotation direction of the wheels moving along the respective sides is reversed, and the wheel B moves while sliding on the two sliding surfaces while stopping the rotation.

The greater the inertial force that attaches to the door just before closing, the more friction is generated in the wheel movement, and the brakes work harder according to the magnitude of the inertial force. Never move. When the closed door is opened, the wheel B moves along the sliding surface Kd of the long hole Hd near the door frame W and the sliding surface Kw of the long hole Hw close to the door frame W. The rotational directions of the wheels moving along the respective sliding surfaces of the wheels coincide with each other, and no resistance is received when the door is opened.
Further, even when the sliding surface K is parallel to the closed door and the moving direction of the wheel is perpendicular thereto, the sliding body KK rotates about the connecting shaft C, so that the moving direction of the wheel B is inclined. And the door becomes easy to open.

The “force for sealing the door” in FIG. 49 will be described.
In most embodiments of the present invention, the “wheel attached to the rotating support shaft provided at the tip of the rotating body rotating around the rotating body rotating shaft” moves in a circular motion, and the tangential direction of the circular motion The force that moves along the sliding surface that is slightly inclined and the wheel presses the sliding surface is the sealing force.
The line of action of the force with which the wheel presses the sliding surface is perpendicular to the sliding surface, passes through or near the rotating body rotating shaft, and the smaller the distance from the rotating body rotating shaft, the smaller the rotating body rotating shaft. The moment that works around is converted into a large sealing force. The moment acting around the rotation axis of the rotating body is the product of the pressing force and the “distance between the line of action of the force and the axis of rotation of the rotating body”. When the “distance between the rotation axes” approaches zero, the pressing force approaches infinity. When the pressing force becomes infinite, the action line of the pressing force passes through the rotating body rotation shaft, and the rotating body cannot rotate and the wheel cannot move.

However, in order for the pressing force to act as a force for sealing the door, it is a condition that the rotating body rotation shaft does not move. By not moving, the pressing force acts on the door while supporting the reaction force of the sealing force. To do.
In the case of FIG. 49, since the position of the rotating body rotating shaft moves, a non-moving fulcrum that supports the reaction force of the sealing force is required, and a sliding surface that faces the sliding surface to be pressed is required. In the case of FIG. 49, a sealing force is generated by simultaneously pressing the sliding surface Kd pressed by the wheel B and the sliding surface Kww that does not move while facing it. In FIGS. 11 and 19 to 22, the sealing force is generated by simultaneously pressing the “sliding surface to be pressed” and the “sliding surface that does not move while facing the surface”.

The wheel moving through the long hole Hw comes in contact with the “sliding surface Kww on the side far from the closed door surface of the long hole Hw” and opposes the “force to rotate the door”, and the “door closed with the long hole Hw” It comes into contact with the sliding surface Kw on the side close to the surface and counters the “inertial force acting on the door”. When the long hole Hw is fixed in parallel to the closed door surface, the long hole Hw is perpendicular to the door surface when fully open and parallel when closed, and counters the “force that rotates the door” as the door approaches closing. And the power to oppose the “inertial force acting on the door” increases. The “wheel moving in the long hole Hw parallel to the closed door surface” is sealed while decelerating.
The spring that is moved by the spring immediately contracts immediately before closing, and the wheel moves in the slot Hw in an instant and does not decelerate. In a door that is moved by an electric motor, “wheels that move in a long hole Hw parallel to the closed door surface” are sealed while decelerating.

FIG. 49 shows a reciprocating slider crank mechanism that converts the rotation of the rotating body into a linear motion of the wheel, and the linear reciprocating motion is substantially parallel to the closed door. The link A rotates about the rotating body rotating shaft Q. The rotating body rotating shaft Q is a connecting shaft QQ provided at the tip of the rotating body J, and the rotating body J revolves around the connecting shaft QQ. When the link A and the rotating body J come close to a straight line, the line of action of the axial force acting on the rotating body J approaches the center of rotation QQ of the link A, and the moment acting around the center of rotation QQ and the large axial force described above. And balance. The axial force acting on the rotating body J increases as the link A and the rotating body J approach a straight line.
As shown in FIG. 49C, when the link A and the rotating body J approach a straight line and the moving direction of the wheels B is substantially parallel to the closed door, the sealing force approaches the maximum value. When opening the door, a force equal to the sealing force acting on the closed door must be applied in the opposite direction. The sliding surface Kd in FIG. 49 is rotatably supported on the door connecting shaft C, and rotates in the same direction as the moving direction of the wheel when the door is opened.

The most necessary spring force to rotate the door is when the latch abuts against the door frame W. When the latch starts to dent, the spring force to rotate the door decreases, In the position where the door is closed after the rotation is complete, the door does not rotate in the reopening direction, and no spring force is required unless the door needs to be pressed against the door to keep it airtight. FIG. 50 shows an embodiment in which the door does not have a sealing force when it is closed, and the door is more easily opened.

In FIG. 50, “the moving body is a rotating body (D) rotatably supported around a rotating shaft (O), and the rotating body (D) and the fixed portion (W) are used as a link. A link device, which is a link device that connects the rotating body (D) and the fixed portion (W) with a plurality of links (J, A, Jc), and which is one of the link devices Each of the two adjacent links (D, Jc) is provided with a contact portion (Gj) that contacts and separates from each other by the rotation of the rotating body, and each of the two adjacent links (D, Jc) is relative to each other. The switchgear characterized by swinging between a small position (Θ1) and a large position (Θ2) where the force acting on the rotating body is integrated or separated.

In FIG. 50, “around the link support shaft C” is provided with a contact Gj that prevents the swing link from rotating in one direction and restricts the movement of the action support shaft or releases the operation support shaft to enable the movement. Thus, the “intersection angle between the swing link Jc and the axis of the working body A” changes due to the rotation of the driven rotating body D, and the working support is delimited by a predetermined opening degree of the driven rotating body. An opening and closing device characterized in that the movement of the axis Cj is restricted or released by restricting the movement of the axis Cj. "

The operation will be described with reference to FIG.
In FIG. 50, a rotating body J having a pulling point P is rotatably supported around a rotating body rotation axis Q provided on the door frame W, and a towed point Cj rotates around a connection axis C provided on the door D. It is provided at the tip of the rotating body Jc that is freely supported. The rotation mechanism in FIG. 50 is the same rotation mechanism as in FIGS. 9C and 9D. The rotating body J is urged in the direction of arrow A in the figure by a torsion spring UV charged to the rotating body rotation axis Q. The door rotates about the pivot axis O of the door in the direction of arrow B in the figure.
The sealing mechanism is the same as the sealing mechanism described with reference to FIG. 49, and the sliding surface Kd attached to the door is rotatably supported around a connection axis Ck provided on the door as in the embodiment of FIGS. The sliding surface Kd rotates around the connecting shaft Ck while being away from the contact Gk and contacting the door frame W from just before closing until sealing. Keep in contact with Gk from fully open to just before closing.

The “long hole Hw parallel to the closed door surface” described in FIG. 49 is divided into two parts by the boundary wall Gk, and the wheel B slides along the sliding surface Kw when the door is closed, It moves along the moving surface Kww.
As shown in FIG. 50 (a), when the wheel B moves along the boundary wall Gh and the sliding surface Kw, a sealing force is applied and the latch is recessed. As shown in FIG. 50B, when the wheel B passes between the boundary wall Gh and the sliding surface Kw, the sealing force does not work at the time of closing. As shown in FIG. 50 (c), when the door is opened, the wheel B performs "a circular motion around the pivot axis O of the door" in the direction of arrow C in the figure. When moving along the sliding surface Kww, the rotating body J rotates in the direction indicated by the arrow D in the drawing to rotate the rotating body Jc so that it hits Gj.

When the door is further opened and the connecting axis C crosses the axis A of the link A, the rotating body Jc does not come into contact with Gj and does not leave in the “range from fully open to immediately before closing (A)”. The position of the traction point Cj is fixed to the door D and remains in the vicinity of the pivot axis O of the door.
When the door is closed, the connecting shaft C performs a “circular movement around the door pivot axis O” in the direction of the arrow C in the figure, but the connecting shaft C is linked in the “range from just before closing to the closing time (i)”. When crossing the axis line Ta of A, the rotating body Jc rotates away from Gj and the rotating body J rotates regardless of whether or not the door rotates.
By linking the link A and the connecting shaft C via a “rotary body Jc that rotates about the connecting shaft C”, a “mechanism in which the sealing device rotates without rotating the door” This is a mechanism for moving the “action point of the force to be moved” far from the vicinity of the pivot axis O of the door.

Even when the door is suddenly accelerated due to a gust of wind, the strong normal door closer decelerates using viscous resistance such as oil, so it is difficult to cause accidents such as strong braking and pinching of the body . Since the present invention employs a means for decelerating without applying resistance, a means for responding to rapid acceleration of the door is desired. 50 and 51 are devices for detecting the magnitude of the inertial force attached to the door, and solve the above problems by interlocking with this device for stopping the door.

51 and 52 are rotating devices that pull the connecting shaft C provided on the door by the link A in the same manner as the rotating device of FIG. 9. If the dynamic inertia is attached to the door, the force to pull the door is attached to the dynamic inertia. The tensile force acting on the link A becomes smaller. The “device for detecting the magnitude of the inertial force attached to the door” is a device for measuring the tensile force acting on the link A. The tensile force acting on the link A can be measured by the deformation of the elastic body interposed in the link A. In FIG. 51, the “elastic body interposed in the link A” is a pressing spring U charged in the connecting portion between the link A and the connecting shaft C. In FIG. 52, the elastic body inserted in the connecting portion between the link A and the connecting shaft C. Torsion spring UV.
As the inertial force attached to the door is larger, the door can be rotated with a smaller traction force, so the tensile force acting on the link A becomes smaller and “deformation of the elastic body interposed in the link A” becomes smaller.

The operation will be described with reference to FIG.
51 and 52, the torsion spring UV is charged into the “fixed support shaft Sw provided on the door frame W” to urge the rotating body J in the direction of arrow A in the figure, and the door D rotates in the direction of arrow B in the figure. In FIG. 51, the link A penetrates the bearing Sz, a pressing spring U is inserted between the end portion of the link A and the bearing Sz, and the rotating body J is urged in the direction opposite to the arrow A in the figure. The bearing Sz is rotatably supported around the connection axis C, and the through hole provided with the bearing Sz is rotatable around the connection axis C, and can cope with a change in the intersection angle between the link A and the door D.
When the inertial force is large as shown in FIG. 51 (a), the length Lu of the push spring U is large, and the end portion Ae of the link A contacts the sliding body KK. As shown in FIG. 51 (b), the end Ae moves along the sliding surface K, and the sliding body KK rotates around the rotation axis I. The contact Gd provided on the door rotates around the pivot axis O of the door. As shown in FIG. 51 (b), when the sliding body KK enters the track where the contact Gd moves, the contact Gd contacts the sliding body KK. Is prevented from rotating.
As shown in FIG. 51 (c), when the inertial force is small, the length Lu of the push spring U is small. The end portion Ae rotates around O, but does not contact the sliding surface K, so the sliding body KK does not rotate. Further, the sliding body KK does not enter the trajectory in which the contact Gd moves, and the rotation of the door is not prevented when the contact Gd hits the sliding body KK.

The operation will be described with reference to FIG.
In FIG. 51, the link A connects the connecting shaft P at the front end of the rotating body J and the connecting shaft Pc at the front end of the “rotating body Jc rotatably supported around the connecting shaft C of the door D”. The “torsion spring UVc mounted around the connection axis C” urges the rotating body Jc in the direction opposite to the direction of the arrow C in FIG.
The link AA connects the connecting shaft Pc at the front end of the rotating body Jc and the connecting shaft Po at the front end of the “rotating body Jo pivotally supported around the door pivot axis O” to rotate the rotating body Jc. To the rotating body Jo.
As shown in FIG. 51A, when the inertial force is large, the torsion spring UVc is hardly deformed and the rotating body Jc is also less rotated. The end portion Je of the rotating body Jo revolves around the pivot axis O of the door at a position away from the door surface. As shown in FIG. 51 (b), “the contact Gd fixed to the door frame W” is in the track where the end portion Je of the rotating body Jo moves, and the end portion Je of the rotating body Jo hits the Gd and the door Rotation is prevented.
As shown in FIG. 51 (c), when the inertial force is small, the torsion spring UVc is largely deformed and the rotation of the rotating body Jc is also large. The end portion Je of the rotating body Jo revolves around the door pivot O at a position close to the door surface. “Gd fixed to the door frame W” is outside the trajectory in which the end portion Je of the rotating body Jo moves, and the end portion Je of the rotating body Jo does not hit Gd and the rotation of the door is not prevented.

51 and 52 show the case where the towed point is attached to the door as shown in FIGS. 9C and 9D, and the detection device is attached to the towed point. 51 and 52, the stop device attached to the door is moved by the detection device attached to the door and is brought into contact with the stop device attached to the door frame to stop the door.
When the tow point is attached to the door frame as shown in FIGS. 9A and 9B, the detection device is attached to the tow point, and the stop device operated by the detection device is attached to the door frame. "Does not enter or exit the trajectory where the door moves" and stops the rotation of the door. The stop device shown in FIGS. 51 and 52 is merely an example, and the present invention is characterized by a detection device that operates by inertia force attached to the door shown in FIGS.

Each of the rotating mechanism or the sealing mechanism of the present invention has its characteristics and can be used not only in the door but also in other industrial fields. The rotating mechanism of the spring-operated door is “the joint of the robot rotating by the electric motor”. It can be applied to the rotation of “part”. The embodiment of FIG. 53 utilizes the rotation mechanism of FIGS. 3 and 4 for the “robot hand”.
For example, the technical feature of FIGS. 3 and 4 is that “the operation of changing the magnitude of the force is possible regardless of whether the driven rotating body is operating or stopped”. The movement of a hand that grabs and moves is realized. Increasing the gripping force in the motion of the hand is accompanied by “the motion of the hand crushing the object”, but it is possible to “increase the gripping force of the hand while gripping the object”.

The present invention is “a technology that continues to rotate with a weak force and rotates with a large force at the final stage,” “There are many operations that require a large force at the final stage. It is an example.
In the embodiment of FIG. 53, the egg is grasped with a small force, and the egg is grasped and lifted with a large force so as not to drop. Even if the size of the egg is different from the place where it is gripped, it must be gripped with a certain force so that it does not break the egg. End up. Regardless of whether the finger holding the egg is moving or stopped, it must be held with a constant force.
If the movement of the finger gripping the egg is driven by the spring mechanism shown in FIGS. 3 and 4, the force to grip the egg can be made constant. It can also be adjusted when releasing the gripped egg with a small gripping force, so that once it is gripped, the egg will not move away until it is released.

The operation will be described with reference to FIG.
53 has a structure in which a rotating body D rotates about a rotation axis O provided on a table W. The rotating body D of the apparatus in FIG. 53 is a door D in FIGS. Is an automatic document feeder for a copying machine. The spring rotation mechanism employed in the embodiment of FIG. 53 is the spring rotation mechanism described in FIGS. 3 and 4, and includes the connection shaft C provided on the rotating body D and the “fixed fulcrum Sw fixed to the table W”. Are connected by a "continuous body AV in which the tension spring V and the link A are connected in series by an intermediate connection shaft Sj", and the rotating body D is moved around the rotation axis O by the force of the tension spring V. It is closed and rotated in the direction.
Rotation is made on the side where the axis axis Zv of the spring is located with the axis line Za of the link A as a boundary, and rotation is prevented at the position where it contacts with Gj, and the axis axis line Zv of the spring When the fixed fulcrum Sw is on the opposite side, the rotating body D rotates away from the contact Gj.

53 shows an embodiment in which the egg Egg is gripped by the tip portion Da of the rotating body D and the tip portion Wa of the table W. FIG. 53 (a) shows a state where the egg is touched, and FIG. 53 (b) shows a state where the egg is gripped. 53 (c) shows a state in which the egg is released. Next, it will be explained that there is not much change in the gripping force for gripping an egg depending on the size of the egg.
If the object Egg to be gripped is large, the gripping Le will be large, the extension of the tension spring V will be large, and the gripping force Fe acting on the object Egg will also be large. If the object Egg to be grasped by inserting the push spring U between the tip Wa of the table W and the table W is large, the force of the pulling spring V and the gripping force Fe increase, but if the gripping force Fe increases, the push spring U is also proportional. Then, even if the object Egg to be shrunk becomes larger, the gripping Le does not increase that much. Therefore, the gripping force Fe does not increase that much.

The contraction of the push spring U represents “the elastic deformation of the buffer body mounted on the grip portion and the distortion of the object to be gripped”. When the compression of the pressing spring U is constant, the grip Le is also constant and the gripping force Fe is also constant. Further, when the compression of the pressing spring U is constant, if the object Egg to be gripped becomes large, the gripping Le becomes large and the pulling spring V and the gripping force Fe become large so that they are not constant.
Relative to the extent to which the spring force increases with respect to the extension of the tension spring V, the stress change of the “buffer body attached to the gripping part or the object to be gripped” increases with respect to the elastic deformation and the amount of strain. A small degree is desirable. In this case, the grip strength does not change much depending on the size of the object to be grasped.

The shoe shown in FIG. 54 is divided into a shoe D and a shoe sole W in two parts, upper and lower, and connected by a pivot O. FIG. 54 (a) shows a state where the shoe has landed, FIG. 54 (b) shows a state where the shoe is about to leave the ground, and 54 (c) shows a state when the shoe leaves the ground. The link A is twisted about the connecting shaft C of the shoe D and is urged by the spring UV in the direction of arrow A in the figure, and the wheel B attached to the tip of the link A is a sliding surface K provided on the shoe sole W. And the shoe D is rotated in the direction of arrow B in the figure. FIG. 54 is an operation explanatory view of the process from the landing of the shoe to the kicking up of the foot, and the rotating mechanism employed is the rotating mechanism of the spring shown in the embodiment of FIG.

As shown in 54 (a), a shoe with a spring attached to the sole is unstable when standing and maintaining a posture, and it is difficult to stand still, but the shoe adopting the spring rotation mechanism of FIG. The spring force hardly acts on the shoe at the time of landing, and even if the shoe rotates slightly as shown in 54 (b) and is slightly opened between the shoe sole, the “force action line Fb and the pivot axis O There is no change in the distance between. Therefore, there is a sense of crushing something at the time of landing, but there is no sense of attaching a spring to the shoe sole in the process from landing to kicking up the foot.
As shown in 54 (c), when the shoe leaves the ground, a large force Fb acts on the sole and kicks the ground. The spring rotation mechanism shown in the embodiment of FIG. 6 adds to the action of kicking up the leg and carrying it forward, and is attached to the leg of the robot.

FIG. 55 shows an embodiment of a speed reducer employing the spring rotation mechanism shown in the embodiment of FIGS. The table W is provided with a pivot O, a rotating body rotating shaft Q, and a fixed supporting shaft Sw, and a four-blade rotating body D, a rotating body J, and a pulling spring V are rotatably supported by each.
The four-blade rotating body D rotates about the pivot O in the direction of arrow B in the figure, and the rotating body J is urged in the direction of arrow A by the pulling spring V through the link A, and the wheel at the tip of the link A The wheel B mounted on the rotary shaft Ib moves along the sliding surface Kd provided on each blade of the four-blade rotating body D. The wheel B applies a pressing force to each blade of the four-blade rotor D to resist the rotation of the four-blade rotor D.

When the position of the fulcrum Sj of the spring in the figure is fixed when the spring is simply attached to the rotating body J, the rotational angle Θj of the rotating body J is moved when the wheel B moves near the tip of the blade. And the expansion and contraction of the spring is increased accordingly, so that the rotational force acting around the rotating body J is large, and the rotational force acting around the rotating body J is small when the wheel B moves near the rotation axis of the blade. . Accordingly, when the wheel B moves near the rotation axis of the blade, the resistance of the rotating body J to the rotation of the four-blade rotation body is small, and a large force is accumulated in the spring as the wheel B moves away from the rotation axis of the blade. A force for returning the blade rotor to the original acts on the tip of the blade, and the resistance applied to the rotation of the four-blade rotor increases. At the same time, the force to return the rotating body J to the original works greatly. Further, when the four-blade rotating body rotates and the wheel B returns from a position far from the rotation axis of the wing to a position close to the rotation axis of the wing, “the force stored in the spring that moves the wheel B from the position near the rotation axis O of the wing” Acts on the four-wing rotating body to accelerate the rotation of the four-wing rotating body D. In this case, both the deceleration and acceleration of the four-blade rotating body are such that the wheel B is far from the blade rotation axis O, and a large spring force acts. When the rotating body J further rotates through the rotations of FIGS. 55 (a) to 55 (c) and returns in the direction opposite to the arrow a in FIG. 55, the wheel B moves along the back surface of the wing. Since the pressing force acting on the four blades is small, the acceleration of the rotation of the four blade rotor in the direction of the arrow B in the figure is small, and the four blade rotor D is moved while the wheel B reciprocates between a place close to and far from the rotation axis O of the blade. Will slow down. However, the deceleration effect is not constant throughout the rotation of the four-wing rotor D, and a strong impact is involved each time the wheel B returns to a location close to the rotation axis of the blade kd.

When the spring rotation mechanism of the embodiment shown in FIGS. 4 and 5 is adopted as the spring mechanism shown in FIG. 55, when the wheel B moves near the rotation axis O of the blade as shown in FIG. 55 (a). As the link A rotates, the position of the fulcrum Sj of the spring moves away from the rotation axis Q of the rotating body J, and the rotational force acting around the rotating body J increases. Further, as shown in FIGS. 54B and 54C, when the wheel B moves near the tip of the blade, the link A reversely rotates and the position of the fulcrum Sj of the spring is close to the rotation axis Q of the rotating body J. By returning to the position, the rotational force acting around the rotating body J is reduced.
As shown in 55 (a), when the wheel B moves near the blade rotation axis, the resistance of the rotor J acting on the four-blade rotor D is increased and decelerated. Also, as shown in FIGS. 54 (b) and 54 (c), when the wheel B moves near the tip of the blade, the rotational force acting around the rotating body J is small, and the rotational resistance of the four-bladed rotating body D is small. Thus, the four-wing rotating body D rotates without being decelerated. Further, when the rotating body J further rotates through the rotations of FIGS. 55 (a) to 55 (c) and rotates in the direction returning to the opposite direction to the arrow A in the figure, the wheel B moves along the back surface of the wing. Therefore, the acceleration of rotation in the direction of arrow B in the figure of the four-bladed rotor is even smaller.

In the process from FIG. 55 (a) to (b), the position of the fulcrum Sj of the spring returns from a place far from the rotation axis Q of the rotating body J to a place close to the place, and the spring force increases. At the same time that the axis of the spring crosses the rotation axis C of the link A, the link A rotates in the reverse direction, and the fulcrum Sj of the spring is returned to a location close to the rotation axis Q of the rotating body J. On the other hand, in the process from FIG. 55C to FIG. 55A where the wheel B returns from a location far from the rotating shaft of the blade to the location where it is close, the location of the spring fulcrum Sj is close to the rotating shaft Q of the rotating body J. In the process of reducing the spring force when moving to a place far from the link A, the link A does not immediately start rotating even if the axis of the spring crosses the rotation axis C of the link A, and the fulcrum Sj of the spring becomes the rotating body J It takes time to move away from the rotation axis Q. This means that when the wheel B returns from a position far from the rotation axis of the blade kd to the position close to the rotation axis, the spring force is not increased and the acceleration does not occur, and the wheel B moves to a position far from the position near the rotation axis of the blade. Sometimes the spring force is slowed down without weakening immediately.
When the spring rotation mechanism of the embodiment shown in FIGS. 4 and 5 is employed as described above, the return energy is stored in the spring when the rotating body J rotates in the direction of the arrow B in the figure, and the four blades are rotated during the return rotation. The rotating body will not accelerate but only decelerate. Compared to the case where the position of the fulcrum Sj of the spring is fixed as described above, the deceleration effect is constant throughout the rotation of the four-blade rotating body D, and the impact with which the wheel B returns to a place close to the rotation axis of the blade is stronger. Becomes smaller.

55 (a) shows a “process in which the wheel B moves from a location close to the rotational axis of the wing to a location far from the wing's rotational axis”. Although the impact is absorbed by the motion of J, the impact is softened at the beginning of the impact, but then follows without resisting the movement of the object. That is, the object can stop moving at the time of collision, but becomes free thereafter.
Similarly, when some object collides with the door D shown in FIG. 48A and an impact load is applied, the door D functions as a shock absorber that absorbs the impact. When an object collides, the object follows the object without resisting, and the braking force increases as time passes. That is, even if the object is free before the collision, it can stop moving after the collision.

48 (a) to (c) of the shock absorber of FIG. 48 is an operation of the shock absorber that stops at a predetermined position so that an object does not finally collide with something. The movement of the shock absorber from FIG. 55 (a) to FIG. 55 (c) is the movement of the shock absorber that allows some object to finally freely move, and FIG. It is also an operation from c) to (a). Further, FIG. 47 is the same as FIG. If the one-way operation damper of the shock absorber shown in FIGS. 47 and 48 is replaced with a two-way operation damper, for example, reciprocation can be counteracted, such as an earthquake shake. The operation from FIG. 48 (a) to (c) and the operation from FIG. 55 (a) to (c) of the shock absorber of FIG. . Every time the direction of the object's swing changes, the speed of the object's movement becomes zero, and when the object stops and starts again, a large force is required at the start, but in these shock absorbers, the direction of the shake changes It acts greatly on "time" and absorbs the energy of the original shaking. However, it will follow the subsequent displacement, and will not store the energy of shaking back. Therefore, there is little shaking back.

FIG. 56 is an explanatory diagram of the structure of the connecting portion between the door and the opening / closing device. The function of switching from the rotating means to the rotating means in the range (ii) ”.
The structure is roughly divided into a device having a sliding surface K shown in FIG. 56A and a wheel B moving along the sliding surface K, and a link device comprising a rotating body J and a link A shown in FIGS. . The connecting shaft P of the two links is outside the two rotation axes C and Sw in the case of FIG. 56B, and is in the middle in the case of FIG. 56C.

The structure of the connecting portion of “the function of rotating the door by transmitting the force F from the opening / closing device” will be described. Both in the case of FIG. 56 (a) and in the case of FIGS. 56 (b) and 56 (c). The link A is a member that transmits force to the door, one end is an action point that transmits force to the door, and the other end is a fixed support shaft Sw that rotates in the direction of arrow A in the figure. This is the force applied to the force.

FIG. 56 (a) will be described.
In the case of FIG. 56 (a), the contact point b between the wheel B and the sliding surface K is the operating point. The line of action of the force Fb at which the wheel B presses the sliding surface K is a perpendicular line standing on the sliding surface K at the contact point b, and passes through the rotational axis Ib of the wheel. The distance between the line of action of the force Fb and the center of rotation Sw is Lf. The force Fb rotates the link A around the fixed support shaft Sw in the direction opposite to the arrow A in the figure. balance. As the distance Lf decreases, the force Fb that balances with the rotational force M increases. When the distance Lf is zero, the force Fb becomes infinitely large, and when the action line of the force Fb and the axis A Za of the link A overlap, the force Fb becomes the largest.

The wheel rotation axis Ib moves circularly around the fixed support shaft Sw. On the wheel rotation axis Ib, the force Fb is broken down into a radial force Fa and a circumferential force Fr. The force Fr acting in the circumferential direction of the circular motion decreases and the force Fa acting in the radial direction of the circular motion increases as the force Fb action line and the axial center line Za of the link A overlap each other.
When the link A rotates about the fixed support shaft Sw, the sliding surface K rotates about the rotating shaft Q. However, the link A rotates in the direction of arrow A in the figure, and the wheel B moves along the sliding surface K. When moving in the direction of arrow B in the figure, the closer to the state where the line of action of force Fb overlaps with the axis A of the link A, the closer the “intersection angle Θa between the sliding surface K and the axis A of the link A” becomes. The closer to the right angle, the smaller the force Fr becomes, and the rotational force M does not participate in the rotation, the force Fa becomes larger and the axial force of the link A becomes larger.
When the sliding surface K that rotates about the rotation axis Q is a door that rotates about the door pivot O, the “rotating means in the range (A)” and the “rotating means in the range (I)” are distances. In a state where Lf is close to zero, “the force Fa is increased even if Fr is small and the rotational force M is small”. Even if a large force is applied in the vicinity of the pivot axis O of the door, the door feels light when the door is opened, and slowly rotates when the door is closed. Further, at the time of sealing, as shown in FIGS. 15 and 16, the wheel moves along the sliding surface with a small force in spite of the large force Fb that presses the sliding surface of the wheel.
When the sliding surface K that rotates about the rotation axis Q is a lid whose rotation axis is horizontal, the force Fa is large even if the distance Lf is close to zero and Fr is small and the rotation force M is small. Although the weight of the lid is large and acts on the wheel, the wheel moves along the sliding surface with a small force to rotate the lid.
When the “intersection angle Θa between the sliding surface K and the axial center line Za of the link A” passes a right angle and changes from an acute angle to an obtuse angle, it does not move in the returning direction, and the sealed door does not open.
The opening / closing device in the middle of rotation is indicated by a solid line, and the opening / closing device at the time of sealing is indicated by a broken line. The action line Fb1 of the force with which the wheel B presses the sliding surface K is a straight line passing through the “contact point b between the sliding surface K and the wheel B” and the rotation axis Ib of the wheel, and the direction along the axis of the link A Thus, it is decomposed into Fa1 which is the radial direction of the circular motion and Fr1 which is the circumferential direction of the circular motion in a direction perpendicular thereto.
And the axial force Fa acting on the link A is balanced. The force point at the other end is attached to the fixed support shaft Sw. The axial force Fa acting on the link A is a rotational force acting on the fixed support shaft Sw. In the case of FIGS. 56 (b) and 56 (c), the applied point at the other end of FIG. 56 (a) is about the fixed support shaft Sw. It is connected to a connecting shaft P provided on the rotating rotating body J, a rotational force acts on the fixed support shaft Sw, an axial force Fa acting on the link A acts, and the axial force Fa acts on the door. Become.

A rotational force acts on the fixed support shaft Sw so that the connecting shaft at the end of each link is displaced, or each link rotates around the connecting shaft. When a “force to move the connecting shaft” is applied, and the rotation or movement motion is restricted, the link is deformed and an axial force Fa is applied to the link A. That is, when the entire link device becomes difficult to move, the axial force Fa acting on each link increases. Therefore, when the link device when the door is sealed is in a movable state, the force for driving the link device, for example, “the rotational force acting on the fixed support shaft Sw” is changed to the motion of the link device.
The force for driving the link device moves the link device in the “range from fully open to just before closing (A)”, and when closing the door, the door is sealed without moving the link device.

56 (a) (b) (c) Not only the respective devices shown in FIGS. 56 (a), 56 (b), and (c), but also each link shaft of the link device described in the present invention rotates or displaces. Is working. Therefore, the node to which the node force for driving the link device is applied may be any of the connecting shafts. For example. 56 (b) and 56 (c), the link device operates even if a rotational force is applied to any of the connecting shafts C, P, and Sw. In each of the embodiments described in the present application, the connecting shaft on which the driving force for driving the link device works is not limited to the connecting shaft shown in the figure, and the link device operates even if a "force for driving the link device" is applied to other connecting shafts. Will do.

Each of FIGS. 56 (a), (b), and (c) has a common point regarding the magnitude of the force F transmitted from the switchgear to the door, and in any case, the axial force Fa acting on the link A seals the door. . In addition, when the line of action of the sealing force acting on the door approaches the state where the link core A and the axis of the link A overlap, a large seal is created when the support shaft on the side opposite to the action point side of the link A is fixed.
In FIG. 56 (a), the action line Fb of the force with which the wheel B presses the sliding surface K increases as it approaches the state where the axis A of the link A overlaps, and in FIGS. 56 (b) and (c). The closer to the state where the axial center line Zj of the rotating body J and the axial center line Za of the link A are in a straight line, the larger the position becomes. Moreover, it becomes so large that the link apparatus approaches the state which cannot move.

As shown in FIGS. 56A and 56B, the action line Fb of the force by which the ring B presses the sliding surface K overlaps with the axial line Za of the link A as shown in FIG. 56A, and as shown in FIGS. The state in which the axial center line Zj of the rotating body J and the axial center line Za of the link A are in a straight line is a state in which the link device is not movable, and is not opened when the closed door is opened. The door is sealed along the way.
When the closed door is opened, the wheel B in FIG. 56 (a) moves parallel to the “closed door surface D0” in FIGS. 56 (b) and 56 (c), and is orthogonal to the direction of the force for opening the door. However, since the link A rotates in both FIG. 56 (a) and FIGS. 56 (b) and 56 (c), there is little resistance to the force for opening the door.

56 (b) and 56 (c) will be described.
56 (a) and (b) and (c), the action line Fj1 of the force acting on the connecting point P is a direction along the axis of the link A, and is a radial direction of the circular motion Fa1 and a circle perpendicular to it. It is decomposed into Fr1, which is the circumferential direction of motion. As the axial core line Zj of the rotating body J and the axial core line Za of the link A are closer to each other, the force acting in the circumferential direction of the circular motion becomes smaller and the force Fa acting in the radial direction of the circular motion becomes larger.

56A and 56C, the link A overlaps the axial center line Zj of the rotating body J and the axial center line Za of the link A as the state where the wheel B and the sliding surface K intersect at right angles in FIG. The closer to the state, the more difficult the link A rotates, and the axial force acting on the link A increases. In FIG. 56 (b), the rotational force acting in the direction of arrow A in the figure around the fixed support shaft Sw is the axial force acting on the link A and the “distance Lf between the axial center line Za of the link A and the fixed support shaft Sw. Therefore, the axial force acting on the link A approaches infinity as the distance Lf approaches zero. In FIG. 56 (c), the axial force Fa acting on the link A approaches infinity as the distance Lf approaches zero, even when the force acting on the support shaft Sw is not limited to the rotational force and an axial force in any direction acts. .

The spring that is continuous with the fixed support shaft Sw will be described.
When the movement u of the fixed support shaft Sw is not restrained, the opening / closing device moves and no large sealing force is generated. Even when the movement u of the fixed support shaft Sw is constrained, during the rotation illustrated by the solid line, the “force that drives the link device” rotates the link device, and the axial force acting on each link is small. When the fixed support shaft Sw supports the axial force Fa acting on the link A while the movement u of the fixed support shaft Sw is constrained and the link device does not move as indicated by a broken line, The directional force Fa grows greatly and a sealing force acts on the door.
That is, the magnitude of the axial force Fa for sealing the door is too small in a state where the movement u of the fixed support shaft Sw is not restrained or in a state where the opening / closing device indicated by the solid line is movable, In a state where the movement u is constrained, as shown by a broken line, when the link device does not move, a large sealing force is generated which is not comparable. The large sealing force is based on the axial distortion of the link A.

As shown in the figure, when the spring U is continuous with the fixed support shaft Sw and the fixed support shaft Sw is movable, the amount of expansion and contraction of the spring becomes a sealing force even if the link A is a rigid body and no distortion occurs. In this case, the magnitude of the sealing force can be adjusted by the position of the support shaft Su of the contact G and the spring U.
As the state shown by the solid line shifts to the state shown by the broken line, the moving amount u of the fixed support shaft Sw increases, the strength of the spring U increases, and the sealing force also increases. This means that the degree of restraining the movement of the fixed support shaft Sw is increased and the movement of the link device is stopped, but the wheel B moves to the sliding surface K in FIG. Accordingly, the force acting in the direction of movement is reduced, the force acting in the direction perpendicular to the axial force is small in FIGS. 56 (b) and 56 (c), and the sliding surface K of the wheel B in FIG. 56 (a). 56 (b) and 56 (c), resistance to movement in the direction perpendicular to the axial force decreases, and the link device shifts to a more movable state as it shifts from the state indicated by the solid line to the state indicated by the broken line. .

In the figure, Rc and Rsw are arcs centered on the connection axis C and the fixed support shaft Sw, respectively. The connection shaft C and the support shaft Sw or C at the end of the link A are moved by the rotation of the switchgear. Represents change.
Further, as the transition from the state indicated by the solid line to the state indicated by the broken line is made, the rate of change of the moving amount u becomes smaller, and the rate of change of the force necessary to continue the movement of the link device becomes smaller.
The region sandwiched between the arcs filled with diagonal lines is a concave lens shape in FIG. 56 (a) and a convex lens shape in FIGS. 56 (b) and 56 (c), and the case of FIG. ) When the movement amount u of the connection axis C and the fixed support shaft Sw is smaller than in the case of (c) and the movement of the connection shaft C and the fixed support shaft Sw is restricted, the movement amount of the connection axis C and the fixed support shaft Sw. Since u becomes a strain and the strain becomes an axial force Fa, the change in the axial force Fa is smaller in the case of FIG. 56A than in the cases of FIGS.

If the movement of the link device continues in the state indicated by the solid line, the movement of the link device becomes easier to continue as the state moves to the state indicated by the broken line. The pushing spring U in the figure stops the movement of the link device, and its force is the weakest in the state indicated by the solid line, and the force for stopping the link device gradually increases thereafter.
It is assumed that the time when the latch is in contact with the door frame W is indicated by a solid line and the time when the door is in close contact with the door stop is indicated by a broken line.
When the latch comes into contact with the door frame W at the end, the rotating means (a) does not have enough force to cause the latch to dent the axial force Fa. Since the force for indenting the latch decreases at a maximum when the latch starts to be indented, the latch abuts against the door frame W when the connecting shaft C or the fixed support shaft Sw at the end of the link A is fixed. If the axial force Fa does not have a force to dent the latch, the opening / closing device stops.

The state in which the movement u of the fixed support shaft Sw is not restrained even when the latch does not switch to the rotating means when the latch abuts against the door frame W and the axial force Fa does not have enough force to dent the latch. Then, even when the sliding surface K shown in the figure does not move, the link device continues to move, and even when the door stops rotating, the opening / closing device moves without stopping, and the axial force Fa gradually grows to open the door. It leads to sealing.
Thus, even when there is not enough force to dent the latch at the end of the rotation range (a), the force for gradually sealing the door is growing in the rotation range (i).
The rotation range of (A) is large and the rotation range of (I) is small. Because the force of different magnitude is acting on the door between the rotation range of (A) and the rotation range of (A), the boundary between the rotation range of (A) and the rotation range of (A) or the rotation of (A) Although the magnitude of the force acting on the door within the range suddenly increases, the force for sealing the door within the slight door rotation range is gradually growing.
The spring U is also a means of growing its own force without rotating the door that received resistance from the latch, and extends the “elapsed time from when the latch contacts the door frame W until the door comes into close contact with the door stop”. It is also a means.

The rigidity of the spring will be described.
The pushing spring U in the figure is a spring that restrains the movement u of the support shaft at the end of the link A. When the rigidity of the spring is zero, the fixed support shaft Sw is free to move and the rigidity of the spring is infinite. When it is large, the fixed support shaft Sw is in a fixed state. If the spring U in the figure is removed and the support shaft Su comes into contact with the end of the link A when sealed, the rigidity of the spring is zero when the latch comes into contact with the door frame W, and the door comes into contact with the door. The spring stiffness is infinite when in close contact.
In this case, unlike the case where the above-described spring is rigid, even if the force for driving the link is weaker than in the above case, for example, when there is no force to start moving the stationary door, the door indicated by the broken line Can be reached when in close contact.

In this case, although the magnitude of the axial force Fa acting on the link A changes abruptly, the wheel B or the connecting shaft P is most easily moved, and the force required for the movement is very small but grows. The axial force Fa is large. That is, the door can be sealed even when the force for driving the link is very small.
The magnitude of the axial force Fa is such that it does not cause the latch to be recessed before the latch is recessed, and the time that the latch is recessed becomes longer as the latch is depressed more rapidly. As in this case, the wheel B or the connecting shaft P is most easily moved, and when the magnitude of the axial force Fa acting on the link A changes abruptly, the impact at the time of sealing is the smallest.

The smaller the rigidity of the spring is, the smaller the force for sealing the door is. The larger the rigidity of the spring is, the larger the force for sealing the door is than “the force necessary for sealing the door”. It is possible to constrain the movement u of the support shaft at the end of the link A at the time of sealing in a state where the rigidity of the spring is zero, so that the force for sealing the door matches the “force required for sealing the door” desirable.
However, when the latch abuts against the door frame W, it is difficult to adjust the axial force Fa to a force that dents the latch. If it is not made larger than this, the rotation of the door stops without the recess being depressed in some cases.

In order to ensure that the door is hermetically sealed, even if the force acting on the door at the time of sealing is set to be far greater than the “force necessary to seal the door”, the end of the link A is supported. When the movement u of the shaft is constrained by a spring, the sealing force gradually increases and becomes larger than necessary to seal the spring U in the middle of expansion and contraction. Although it is not necessary to apply a force to the door when the door comes into contact with the door frame W, the door is brought into contact with the door frame W while the spring U is expanded and contracted.
When the force applied to the door at the time of sealing matches the “force required to seal the door”, there is no impact sound at the time of sealing, and a wasteful force that works more than the “force required to seal the door” is an impact sound. Changes to.
In order to ensure that the door is hermetically sealed, if the axial force Fa is larger than necessary, the impact sound when the door comes into contact with the door frame W increases. Can be kept small.

The spring U that restrains the movement u of the fixed support shaft Sw works in the direction opposite to the axial force Fa, and increases as the opening / closing device rotates. However, the spring U is charged inside the opening / closing device. Is not supported by the door frame W, and the direction of the force of the spring U is the rotational axis direction of the link A and does not resist the rotational force acting around the rotational axis of the link A. The directional force Fa is all transmitted to the door without being reduced. The force of the spring U acts as an internal force and is transmitted to the door in the direction of sealing the door.

The impact sound at the time of sealing is not how small the magnitude of the “sealing force of the door” is, but is equal to the “force required to seal the door”.
The magnitude of the inertial force attached to the door at the time of sealing differs depending on the “opening angle of the door when the hand is released from the door”. If the door is rotated by the inertial force at the time of sealing, the magnitude of the force to seal the door Therefore, the problem is how to start the sealing operation in a state where the inertial force is lost, and to ensure that the sealing operation is constantly performed by applying a constant sealing force.

The structure shown in FIG. 56 (a) is the structure shown in the embodiment of FIG. 6, the structure shown in FIG. 56 (b) is the embodiment shown in FIG. 40 (c), and the structure shown in FIG. 21 (c) is the structure shown in the embodiment of FIG. 49 (d), and in the embodiment of FIGS. 46 and 49, the connecting shaft P at the tip of one of the links in FIGS. This is a structure that reciprocates in a passage provided in the other link.
57-60 of the below-mentioned Example is the structure of Fig.56 (a), Comprising: When switching from (a) rotation means to (ii) rotation means, wheel B is "closed door surface D0". And move away from the pivot axis O of the door. Embodiment The structure of FIGS. 61 and 62 is the structure shown in FIG. 56 (b), and the structure of the embodiment FIG. 333 is the structure shown in FIG. 56 (c).
The spring U shown in FIG. 56 (a) is shown in FIGS. 57 (f) (e), 70 and 71.

56 (a), (b), and (c), the “function for switching the switching device from the rotating means in the range (A) to the rotating means in the range (I)” will be described.
In FIG. 56 (a), when the sliding surface K is pivotally supported about the rotation axis Q, and the rotational force M in the direction of arrow A in the figure acts around the fixed support shaft Sw, the rotating body J When the crossing angle Θa between the axial center line Zj of the link A and the axial core line Za of the link A is an acute angle, the rotation of the link A in the direction indicated by the arrow a in the figure is suppressed.
For example, as shown in FIG. 6 and FIG. 21, when the rotational force in the direction of arrow A in the figure is acting around the fixed support shaft Sw, the wheel B is in the vicinity of the pivot axis O of the door and the movement of the wheel B is reduced. It is fastened. 56 (a) as well as FIGS. 6 and 21, it is assumed that the wheel B moves in the direction of the arrow B in the figure while pressing the sliding surface K along the sliding surface K by the rotational force M. As B approaches the position of B2, the crossing angle Θa increases, and the wheel B becomes more easily moved on the sliding surface K.
The above deterrence is released when the obtuse angle is reached.
Assuming that the sliding surface K is Rsw1 around the fixed support shaft Sw, the wheel B moves greatly in an instant without pressing the sliding surface K as in the case of FIGS. . In this case, the fixed support shaft Sw does not move, and no force acts on the sliding surface K.
As shown in the embodiment of FIGS. 7 and 20, when the axial force is applied to the link A and the wheel B presses the sliding surface K, the wheel moves in the same manner. ) Functions as a means for switching to the rotation means within the range.

56 (b) and 56 (c), it is assumed that the state where the intersection angle Θa between the axial center line Zj of the rotating body J and the axial center line Za of the link A is illustrated by a solid line is positive, and the state illustrated by a broken line is zero. When the crossing angle Θa changes from positive to negative, that is, when the axial center line Zj of the rotating body J crosses the axial center line Za of the link A, the direction of the arrow A in FIG. Rotation is inhibited, and the inhibition is released when it turns from negative to positive.
When the crossing angle Θa is negative in the rotation range of (A) as in the embodiment shown in FIG. 50, the link A blocks the movement of the connecting shaft P while being in contact with the contact G, and the crossing angle Θa becomes positive. When rolling, the link A hits and moves away from the G so that the connecting shaft P moves. That is, the rotation means in the range (A) is switched to the rotation means in the range (I).

In FIG. 57 (e), the mounting shaft C of one side A of any two adjacent links constituting the above-mentioned link device is relatively movable and is attached to the other D so that force is temporarily transmitted from one side to the other. Switchgear characterized by being electrically insulated.
Different functions are added to the respective embodiments by movably mounting the wheels or the sliding surfaces in the respective embodiments with sealing devices or insulating means sliding surfaces. In the case of FIG. 57, by rotating the sliding surface, the movement of the wheel can be moved far from the vicinity of the door pivot in parallel with the closed door surface, and the sealing action point can be greatly separated from the door pivot. In addition, the full opening angle of the door can be expanded.
57D and 57E, the sliding surface is movable by revolving around Ij and absorbs inertial force or rotation in the opening direction. In FIG. Will grow. In the case of FIG. 78, when the sliding surface rotates, the gradient of the sliding surface K changes in the opening direction. By rotating the sliding surface, the rotational speed of the driven rotating body is reduced, or the direction in which the driven rotating body is urged is changed to prevent sealing.
“One of the urging means is movably attached along the track, and has releasable restraining means for restraining movement of one of the urging means, and part or all of the rotation of the drive rotating body. Opening and closing device that is not transmitted to the driven rotating body "

The embodiment shown in FIG. 57 (f) is a door D in which the sliding surface K in FIG. 56 (a) rotates around the pivot axis O of the door, and the wheel B in FIG. 56 (a) moves along the door surface. Then, the door is rotated, and the door is sealed so that the pressing force Fb works at right angles to the “closed door surface D0”.
In this case, the distance B is reduced in most of the “range from fully open to just before closing (A)”, and the wheel B is in a short rotation range of “range from just before closing to when closing (yes)”. The door moves to a position far from the door pivot O and seals the door, but the distance L between the line of action F of the force acting on the door and the door pivot O is too large between L90 when the door is fully opened and L0 when the door is closed. There is no difference.
When the door weight is large, the force to rotate the door increases in the “range from fully open to just before closing (A)”. Also, even when the door weight is small, the force to seal the door is small. Therefore, there is no need to make much difference between L90 when the door is fully opened and L0 when the door is closed.

In the embodiment shown in FIG. 57 (f), as the fixed support shaft Sw is located as far as possible from the closed door surface, the wheel B becomes closer to a linear track parallel to the closed door. B stays in the vicinity of the pivot axis O of the door from the fully open state to just before closing, and moves instantaneously immediately before closing.
In the embodiment shown in FIG. 57 (f), in order to increase the distance L0, the full opening angle of the door D may be reduced or the link A may be lengthened. However, there is a problem that the apparatus becomes large. Further, when the “closed door surface D0” is opened, there is a problem that the direction of the force received by the wheel B and the moving direction are orthogonal and difficult to open.
57 (a) to 57 (c) or (d) (e), the sliding surface K, which is a component of the sealing device, is provided on the door D as in the embodiment shown in FIGS. Further, it is attached to the connecting shaft C so as to be rotatable, and has a feature that the door B is kept in contact with the sliding surface K by increasing the full opening angle of the door and increasing L0 at the time of closing.
The sliding surface K is substantially parallel to the “closed door surface D0” when sealed, and the moving direction of the wheel B moving along the sliding surface when sealed is substantially parallel to the “closed door surface D0”. However, when the sliding surface K rotates around the connection axis C, the closed door can be easily opened.

FIG. 57 shows a slider link shown in FIG. 56 (a) having a link A that rotates about a fixed support shaft Sw provided on the door frame and a sliding surface K that rotates about a connection shaft C provided on the door D. 56 is a structure in which the length of one of the “two links connecting the connection shaft provided on the door and the fixed support shaft Sw provided on the door frame” shown in FIGS. 56 (b) and 56 (c) is changed. .
A wheel B is mounted on a rotating shaft Ib of a wheel provided at the tip of the link A, and the wheel B moves along the sliding surface K. In the embodiment in which the leaf spring VW is charged around the connecting shaft, as shown in FIG. 57 (a), the sliding surface K revolves around the pivot axis O of the door while rotating in the direction of arrow A in the figure. The door D is rotated in the direction of arrow B in the figure. In FIG. 57 (a), the operation of the door D, the rotating body J, the link A, the position of the connecting shaft C, and the fixed fulcrum Sw in the process from when the door opening angle .THETA. The change in the position of the door is represented by a dotted line, and the state during the closing of the door is represented by a solid line.

As shown in FIG. 57 (a), the connecting shaft C revolves around the wheel B and rotates the door in the “range from fully open to just before closing (A)”. The wheel B is at the tip of the sliding surface K and is far from the center of rotation C of the sliding surface K, and the force with which the wheel B presses the sliding surface K is small.
The shape of the sliding surface K is a shape that coincides with the circular orbit of the wheel that moves around the fixed fulcrum Sw, and as shown in FIGS. 57 (b) and (d), the door is the same as in the embodiment of FIG. Immediately before closing, when the sliding surface coincides with the circular track on which the wheel moves around the rotation axis, “wheel B staying at a position far from the rotation fulcrum” instantaneously moves to the vicinity of the rotation fulcrum.
Even if the shape of the sliding surface does not coincide with the circular orbit of the wheel, the wheel B can move even if it is a concave surface having a smaller curvature or a linear surface having a larger curvature.

57 (a), (b), and (c) are different from the structures shown in FIGS. 57 (d) and (e), FIGS. 57 (a), (b), and (c) hit both sides around the fixed fulcrum Sw. When the vehicle is closed, the wheel hits and comes into contact with G2, and the movement of the wheel B is prevented. In FIGS. The movement of B along the sliding surface K is limited by a recess Kc provided at a position near the rotation center C of the sliding surface K.
The operation of “range from fully open to immediately before closing (A)” in the structure shown in FIGS. 57D and 57E is the same as FIG.

As shown in FIGS. 57 (b) and 57 (d), the wheel B moves to a position closer to the center of rotation C of the sliding surface K in the “range from immediately before closing to the closing time (i)”. The force that presses the sliding surface K increases.
57 (a), (b), and (c), the sliding surface K is a lever in which the wheel B is a fulcrum and the connection shaft C is an action point. The distance between the fulcrum and the fulcrum changes, the turning radius of the action point decreases, and the turning moment is converted into a large axial force. As the sliding surface K rotates about the connecting shaft C, the wheel B approaches the connecting shaft C and the sealing force gradually increases and acts on the door.

In the structure shown in FIGS. 57A, 57B, and 57C, the rotation of the sliding surface K is directly connected to the rotation of the door, and the rotation of the sliding surface K stops when the door stops rotating. When the latch abuts against the door frame W, the wheel B is far from the center of rotation C of the sliding surface K, and the rotational force of the sliding surface K is less than or equal to the “force that dents the latch inside the door” Thus, the rotation of the sliding surface K and the rotation of the door stop. If the wheel B does not move to a position close to the center of rotation C of the sliding surface K before the latch contacts the door frame W, the door stops rotating. The force acting on the door is increased and the closing speed is accelerated rapidly.
In the structure in which the rotation of the sliding surface K is directly connected to the rotation of the door, such as the structure shown in FIGS. 57 (a), (b), (c), FIG. 13, and FIGS. In order to reduce the closing speed as quickly as possible, the “time from when the force acting on the door switches greatly until the latch abuts against the door frame W” can be reduced as much as possible. There is no other way to do it.

The embodiments of FIGS. 3 to 12 and FIGS. 14 to 18 do not directly connect the operation of the sealing device and the rotation of the door. The sealing device operates regardless of the rotation of the door, and the force acting on the door increases. The door can be sealed. However, even in this case, if the operation of the sealing device starts when the latch contacts the door frame W, the sealing device operates regardless of the rotation of the door, but after the latch contacts the door frame W and the door stops rotating. Then the operation of the sealing device does not start.
That is, even in this case, unless the start of the operation of the sealing device is before the latch comes into contact with the door frame W, the rotation of the device and the rotation of the door are stopped, and FIGS. 19 to 26, it is inevitable that the closing speed rapidly accelerates at the end of the door rotation.

57 (d) and 57 (e), the connecting shaft C is provided on the rotating body Jc, and the rotating body Jc rotates about the rotating support shaft Ij provided on the door D. A pressing spring U is mounted between the rotating body Jc and the door surface. The force of the apparatus is transmitted to the door via the push spring U, not the structure that directly connects the rotation of the apparatus and the rotation of the door.
When the latch abuts against the door frame W as shown in FIG. 57 (d), even if the wheel B is far from the center of rotation C of the sliding surface K and there is no force to rotate the stopped door, If there is a force for contracting the push spring U, the sliding surface K continues to rotate, and the wheel B moves to a position closer to the rotation center C of the sliding surface K. The force acting on the door increases after the latch comes into contact with the door frame W, and the door is brought into close contact with the door by denting the latch with the force increased by the rotation of the sliding surface K instead of the rotation of the sliding surface K. Let The closing speed does not accelerate immediately before closing.

57 (d) and 57 (e), “the contact point b between the sliding surface K and the wheel B” is in the middle of the two rotation shafts of the rotation support shaft Sw and the connection shaft C, and the two axial lines Zk and Za At the beginning of bending, a large force is required to extend the distance between the two rotating shafts, and the rotation of the two links K and A may stop. In order to prevent this from happening, one of the rotation shafts Sw or C of the two links is movably attached. When the space between the two rotation shafts Sw and C is extended, the rotation of the two links continues even if the rotation of the door is stopped.
The smaller the rigidity of the push spring U inserted into the transmission mechanism of the apparatus, the more the apparatus continues to rotate even if the door stops rotating. When the rigidity of the push spring U is zero, that is, when the push spring U is removed in FIGS. 57 (d) and 57 (e), there is no force to rotate the door just before closing, as shown in FIG. 57 (d). The door continues to rotate due to the inertial force attached to the door, even when the movement stops and the device stops. Regardless of whether the latch contacts the door frame W, after the door decelerates or stops, a gap is created between the rotating body Jc and the door surface, and the sliding surface K rotates in a state close to no load. The wheel B is moved to a position close to the connection axis C.

Thus, when the force of the spring that rotates the door at the end of the range (A) is weakened and the force acting on the door in the range (A) is largely switched, the latch abuts the door frame W. Even if the latch is recessed, it has the effect of reducing the closing speed. Just before the closing, a part of the sliding surface K comes into contact with the door frame W and the sliding surface K rotates to move the wheel B toward the connecting shaft C. If it is made to do, the starting time of the wheel B can be limited, and if the work in that case will reduce the closing speed, it will become a door.

57 (d) and (e), when the wheel B moves along the recess Kc, FIG. 56 (c) the axial center lines Za and Zj of the two links are straight from the bent state about the connecting shaft P. As approaching, the axial center line Zk of the sliding surface K and the axial center line Za of the link A approach a straight line from a state of being bent about the rotational axis Ib of the wheel.
The line of action of the force with which the wheel B presses the sliding surface K is a straight line passing through the “contact point b between the wheel B and the sliding surface K” and the rotational axis Ib of the wheel. It changes as it moves along the wheel B. When the wheel B comes into contact with the recess Kc, the line of action of the force acts toward the door pivot O to decelerate the closing speed.
Then, as the recess Kc revolves around the connecting axis C with the wheel B, the action line Fb of the force pressing the wheel B moves away from the vicinity of the door pivot O, as shown in FIG. 56 (c). As in the case, it becomes a strong sealing force and acts at a position far from the pivot axis O of the door.

As the distance Lf between the force action line F and the center of rotation C approaches zero, the magnitude of the axial force F approaches infinity, and the ratio of the magnitude of the force for rotating the door and the force for sealing is also infinite. Approaching large.
When the door is sealed, the link stops rotating. Since the closed door cannot be opened if the two shaft cores are completely aligned when the door is sealed, the door is sealed when the two shaft cores are slightly bent.

FIG. 57 (c) shows the positions of the connecting shaft C, the sliding surface K, and the wheel B at each time point in the process of closing the door, and C5 indicates the rotation fulcrum of the wheel B instantly when the door is closed. C30 indicates the position of the connecting shaft C when the wheel B returns to a position far from a position close to the rotation fulcrum when the door is opened.
When the wheel B moves in the vicinity of the rotation fulcrum in the process of closing the door, the sliding surface K has little force to press the wheel B and does not resist the wheel movement. However, in the process of opening the door, the force with which the sliding surface K presses the wheel B greatly resists the movement of the wheel. Therefore, in the process of opening the door, “the opening angle of the door when the wheel B returns from a position close to the rotation fulcrum to a position far from the rotation fulcrum” is shown in FIG. 57 (b) in the process of closing the door. And the door opening angle when moving to the vicinity of the rotation fulcrum.

As shown in FIGS. 57B and 57D, immediately before the wheel B instantaneously moves to the vicinity of the rotation fulcrum, the action line F10 of the force acting on the door passes near the pivot axis O of the door, and the door Decelerate just before closing. At this time, the force acting on the door does not have the force to rotate the door, but the dynamic inertia works and the door continues to rotate. When this dynamic inertia works and the hand is released at a position where the door continues to rotate, the rotation of the door stops. In other words, when the hand is released from the position where the door is fully opened, sealing is achieved, but when the hand is released from the position where the door is slightly opened, sealing is not achieved.
Fig. 57 (b) shows that when the hand is released from the position where the door is slightly opened, the door remains stationary while it is still open, and the door can be opened a little to respond to an outpatient. “The door opening angle when the wheel B moves in the vicinity of the rotation fulcrum in an instant” and “The door opening angle when the wheel B moves to a position far away from the rotation fulcrum” shown in FIG. If they are different, the position where the door continues to rotate due to dynamic inertia is applied, and if the door is closed with the hand in the process of closing, the door may remain stopped, but the process of opening the door When you release your hand, the door will always begin to close.

As the biasing means for the door of the present invention, there are a pull spring V, a push spring U, and a torsion spring UV. FIG. 57 shows an embodiment in which a leaf spring is employed. One of the fulcrums at both ends of the spring is attached to the sliding surface K and the other is attached to the door D in the vicinity of the connecting shaft C. As shown in FIG. 57 (a), in the “range from fully open to just before closing (A)”, the leaf spring VW is bent in a U shape, and the support reaction force acting on both ends of the spring is in the axial direction of the spring. The leaf spring VW is substantially linear in the “range from right before closing until closing” (i), and the support reaction force acting on both ends of the spring works in the axial direction of the spring. Strongly acts on the door.
The rotation of the sliding surface K is small in the “range from fully open to just before closing (A)”, and large in the “range from just before closing to the closing (yes)”, as shown in FIG. Even when the leaf spring VW is bent in a U shape when the latch comes into contact with the door frame W, the leaf spring VW approaches a straight line when the door is sealed as shown in FIG. The force acting on the door gradually increases and grows into a force that seals the door.

The structure of FIG. 58 is configured by linking the link A of FIG. 57 with two links of the rotating body J and the link A, and the position of the action point b90 at the time of sealing is separated from the pivot axis O of the door. . In FIG. 57, the wheel B has a circular motion around the fixed support shaft Sw, but in FIG. 58, the wheel B can move freely.
The embodiment shown in FIG. 49 is the same as the structure of FIG. 58, but in the structure of FIG. 58, the rotating shaft of the rotating body J is attached to the door frame W at a position far from the pivot axis O of the door. In the embodiment shown in FIG. 49, the door is attached at a position close to the pivot axis O of the door. The wheel B moves along the sliding surface Kd to which the door D is attached and the sliding surface Kw to be attached to the door frame W at the same time, thereby fixing the track of the wheel B.

In the structure shown in FIG. 58, the two springs V1 and V2 are used to keep the track of the wheel B at a position close to the door pivot O in the "range from fully open to just before closing (A)". In the range until the closing time (i) ", it moves to a position far away from the pivot axis O of the door, and the near position and the far position at the boundary of the range (a) and (ii) To make a round trip. The two pulling springs V1 and V2 in FIG. 57 do not pull the wheel B directly to cause linear movement like the springs in FIGS. 59 and 60 to be described later, but rather cause the link to move circularly. I'm not sorry.
In the structure of FIG. 58, the sliding surface Kw of FIG. 49 attached to the door frame W by two pulling springs V1 and V2 is omitted.

FIG. 57 (a) is an explanatory diagram of the door operation, showing the position at each moment of the closing process of the wheel B, the rotating body J, and the link A, and the solid line is a position slightly opened from the door D0 where the door is closed. Shows the state. The tension springs V1 and V2 urge the rotating body J to rotate in the direction indicated by the arrow B in the figure and the link A to rotate in the direction indicated by the arrow C in the figure.
When the door B is closed, the force of the tension spring V2 is strong until the wheel B reaches the position of B10 indicated by a solid line from the position of B90 when fully opened, and the intersection angle Θad between the link A and the rotating body J is increased while the tension spring V1 is extended. Decrease.
As the door D rotates, the “intersection angle Θa between the link A and the sliding surface K” increases, and the wheel B easily moves away from the door pivot O as described with reference to FIG. The state indicated by the solid line is a moved state. Since the tension spring V2 is weakened, the tension spring V1 becomes relatively strong, and the rotating body J rotates in the direction of arrow B in the figure. The contact point b moves away from the pivot axis O of the door and at the same time approaches the rotation axis Q, and the force acting on the door is strengthened by the lever principle.

As indicated by the solid line, when the door is closed, the wheel B moves in the direction indicated by the arrow E in the figure. When the door is opened, the wheel B moves in the opposite direction to the arrow E in the figure. Since it moves in the opposite direction, as described in FIG. 57 (c), the rotation angle of the door when the wheel B returns to the position near the pivot axis O of the door is equal to the rotation angle of the door when the door is closed. large. As in the case of FIG. 57, in the case of FIG. 58, just before the door is closed, the direction of the force acting on the door is directed to the pivot axis O of the door, or resistance is temporarily applied to the rotation of the door. Even if the door is set to a force smaller than the force to rotate the stopped door again, the door closing speed can be reduced, or the door can be opened even if the door is opened and released. It will never stop.

FIG. 58D is a diagram showing a state in which the door D is closed. Unlike the structure of FIGS. 58A to 58C, the sliding surface Kw is attached to the door frame W, and the sliding surface is attached to the door D. Kd and sliding surface Kdd are attached. Further, instead of the tension springs V1 and V2, the torsion spring UV1 is attached to the rotating shaft Q and the torsion spring UV2 is attached to the connecting shaft P, respectively. The wheel B or BB is attached to the wheel rotation axis Ib, and the wheel B is sandwiched between the sliding surfaces Kd and Kdd. The sliding surface Kd is rotatably supported by the rotation shaft Ik, and the spring U described in FIG. 56 is inserted between the sliding surface Kd and the door surface.
The contact G prevents the sliding surface Kd from rotating in the direction of the arrow in the figure. When the inertial force acts strongly during sealing, the wheels B and BB come into contact with the sliding surfaces Kw and Kdd, respectively, and the rotation of the door is prevented. Stop. That is, the inertial force acting on the door is converted into a braking force.
When the two wheels B and BB are fixed to the rotation shaft, when the two wheels B and BB move along the two sliding surfaces Kw and Kd at the same time, the respective rotation directions are opposite to each other, the movement of the two wheels B and BB The brake is applied.
When a strong wind is received when the door is closed, the time required for the movement of the two wheels B and BB becomes longer, and a large force is applied within the required time, so that the rotation of the door stops and does not seal. In this way, a fingernail accident can be prevented.

FIG. 60 shows an opening / closing device in which a spring (V) is attached in place of one of the links constituting the link device.
In FIG. 60, the expansion joint is two links A, wheels B3, and a tension spring V. In FIG. 73, a driven rotating body that is rotatably supported around the driven shaft, a fixed portion that fixes the driven shaft, and a string or a spring that provides tensile force by expanding and contracting are connected in series. A fixed support shaft provided with a string and a pulley and having one end of the "string or string connected in series with the spring" on the connecting shaft provided on the driven rotating body and the other end on the fixed part An opening and closing device characterized in that the "string or string connected in series with the spring" rotates while moving along the pulley.

In the embodiment shown in FIGS. 59 and 60, a linear track parallel to the closed door surface is provided on the door frame W, and the slider moves along the linear track. In FIG. As in the case where the link A is located as far as possible from the closed door and the length of the link A is increased, the point of action of the force acting at the time of sealing is far from the pivot axis O of the door. In FIG. 57, the link A rotates and the operation range protrudes from the “closed door surface” in a circle in plan view. On the other hand, in the embodiment shown in FIGS. 59 and 60, the link A does not protrude in a plan view from the door surface where the operation range is closed due to the parallel movement.
The embodiment of FIGS. 59 and 60 is an opening / closing device characterized in that the link A functions as a lever only when the link A is sealed, and the link A has a wheel B2 serving as a fulcrum of the lever or a slide that moves along the same. A surface K2 is provided. The wheel B2 and the sliding surface K2 are in contact only when sealed. When the closed door is opened, the wheel B2 is instantaneously separated from the sliding surface K2.
59 and 60, the wheel B1 is attached to one end of the link A, and the wheel B1 moves along K1 attached to the door D. As described with reference to FIG. 56 (a), the door is rotated slightly before closing. To move from a position close to the pivot axis O of the door to a position far from the door.
Due to the large operation of the “switching means”, the wheel B2 and the sliding surface K2 can be moved relatively disengaged relatively.
A wheel B3 is attached to the other end of the link A, and the wheel B3 moves along the "sliding surface K3 of a linear track parallel to the closed door surface", and changes the moving direction to a substantially right angle when sealed.
By changing the moving direction to a substantially right angle at the time of sealing, a force acts on the lever, ie, the point B3 of the link A in a right angle direction, and a force acts on the lever, ie, the point of action B1 of the link A, in a direction perpendicular thereto. When opening the closed door, the action point B1 of the link A moves in a direction perpendicular to the direction away from the "closed door surface", and the force point B3 of the link A is perpendicular to the direction approaching the "closed door surface". Move to. When the applied point B3 of the link A moves along a path parallel to the “closed door surface” as in Patent Document 3, the door can be closed but cannot be opened. The door can be opened when the force B3 of the link A is rotatable about the fulcrum B2.

The force required to move the slider becomes smaller when the number of means for forcing the slider to move along the “straight track parallel to the closed door surface” is minimized. The wheel B2 and the sliding surface K2 are in contact only when sealed, and when the closed door is opened, the wheel B2 is instantaneously separated from the sliding surface K2, so that the wheel B does not move along the sliding surface as much as possible. If so, the spring force is small.
When the wheel B moves along the sliding surface, the spring force is dispersed, so it is necessary to increase the spring force. When the wheel force is increased, the rotational resistance of each connection point of the link increases, and the spring The result is to increase the power of. When the door is opened, the door feels heavy.

FIG. 59A shows a fully opened state, FIG. 59C shows a fully closed state, and FIG. 59B shows a state immediately before closing.
In FIG. 59 (a), the wheel B1 stays at the end of the sliding surface K1 provided on the door D on the side close to the pivot axis O of the door, and as the door D closes as shown in FIG. The crossing angle Θa of the sliding surface K increases and becomes an obtuse angle, and the wheel B1 starts moving.
The sliding surface K3 is rotatably supported by a rotation shaft Ik provided on the door frame W, and the recess KK is provided near the rotation shaft Ik of the sliding surface K3. As the wheel B3 approaches the recess KK, the force of the spring Va is weakened, and the “force for rotating the sliding surface K3 in the direction indicated by the arrow B” of the spring Vk is increased. The sliding surface K3 rotates greatly when sealed.
When the door is sealed, as shown in FIG. 59 (c), the recess KK revolves around the rotation axis Ik, whereby the wheel B1 moves linearly and the wheel B2 and the sliding surface K2 come into contact with each other. The contact point b1 between the wheel B1 and the sliding surface K1, the contact point b2 between the wheel B2 and the sliding surface K2 fixed to the door frame W, and the contact point b3 between the wheel B3 and the sliding surface K3 are the lever action point, fulcrum, It functions as a power point. The action lines acting on the contacts b1, b2, b3 are substantially perpendicular to the “closed door surface D0”.

In the case of FIG. 60, the wheel B2 which becomes a lever fulcrum when sealed is fixed to the door frame W, and the sliding surface K2 is attached to the link A. A wheel B1 is mounted at one end of the link A, and a recess KK is provided at an end close to the pivot axis O of the door on the sliding surface K1 on which the wheel B1 moves.
The wheel B3 attached to the other end of the link A moves along the sliding surface K3 fixed to the door frame W, and moves away from the sliding surface K3 when sealed. The force of the tension spring V is distributed to the force pulling the link A and the force pressing the sliding surface K3 when moving along the wheel B3 or the sliding surface K3. Becomes the force pulling the link A.
When the door is opened, the wheel B3 moves along the sliding surface K4 facing the sliding surface K3.

FIG. 60A shows a fully open state, and FIG. 60D shows a fully closed state. (B) and (c) show a state in the middle of closing. As the door D is closed, the “intersection angle Θa of the link A and the sliding surface K” increases. In the range (A) ", it is included in the depression KK and stays at a position near the pivot axis O of the door. As shown by the dotted line in FIG. 60 (d), immediately before closing, the wheel B1 escapes from the recess KK and moves from the side near the pivot axis O of the sliding surface K1 toward the far side.
Immediately before closing, the wheel B1 can come out of the recess KK by contacting the door frame W. In this case, the force acting on the door works to make the wheel B1 escape from the recess KK. The “door rotation angle Θd” until the latch abuts against the door frame W after the force that is decelerated and the force acting on the door increases becomes small.

As the door is opened, as shown by a broken line in FIG. 60B, the “intersection angle Θa between the link A and the sliding surface K” increases, becomes an obtuse angle, and the wheel B1 is far from the door pivot O of the sliding surface K1. Start moving from side to side.
Also in the case of FIG. 60, as described in FIG. 57 (c), the door rotation angle door Θd when the wheel B returns to a position near the pivot axis O of the door when the door is opened is the same as that of the wheel when the door is closed. B is greater than the door rotation angle door Θd when leaving the position near the door pivot O.

The link device of the present invention is constituted by three or less rigid bodies of a driven rotating body, an action body, and a swing link in addition to two rigid bodies of a driven rotating body and a fixed portion. ) Range rotation means ”and“ (ii) range rotation means ”, and further“ switching means ”,“ linkable and releasable restraining means by contact with it ”or“ sliding surface ” A releasable restraining means by a wheel moving along with it is provided.
A link device having four or more other rigid bodies is also conceivable. However, as the number of rigid bodies constituting the rigid body increases, the number of trajectories that restrain their movement increases and the movement of the apparatus becomes worse. Further, as the number of rigid bodies increases, the number of connecting shafts increases and the rotational resistance around the connecting shafts increases.
The link device provided with the “releasable restraining means by the sliding surface and the wheel moving along it” reduces the number of other rigid bodies by one and reduces the rotational resistance around the connecting shaft by one. become.

A link device provided with a “releasable restraining means by a link and a contact with the link” connects the driven rotating body and the two rigid bodies of the fixed portion by the three rigid bodies of the driving rotating body, the acting body, and the swing link. 61 and 62 are connected by two rigid bodies, that is, a drive rotating body and an action body, and those connected by two rigid bodies are described in FIGS. 61 and 62 (supported rotatably around the drive shaft). An opening / closing device that transmits the rotation of the drive rotator J to the driven rotator D (supported rotatably around the driven shaft) and includes a fixing portion W (fixing the driven shaft). An actuating body A is connected to a driving support shaft P (provided at the end opposite to the driving shaft) of the driving rotating body J, and is provided at an end portion of the operating body (opposite to the driving support shaft). ) One of the drive shaft and the drive shaft of the drive rotating body is attached to the fixed portion W, A structure that attaches to the driven rotating body D, includes a door stop that contacts the driven rotating body D and prevents one rotation of the driven rotating body D, and a distance between the working support shaft and the driving shaft The drive rotator D is rotated in a direction (approaching the door stop) while reducing the rotation of the drive rotator J, while maintaining the state where the shaft core line of the drive rotator J and the axis core line A of the working body substantially overlap. Rotating to bring the driven rotating body D into close contact with the door stop. "A means for making a straight line from a bent state of the force action line and the link core line".
Alternatively, as shown in FIGS. 63 and 64, the rotation of the drive rotator J (supported rotatably around the drive shaft) is rotated by the driven rotator (supported rotatably around the driven shaft). D is an opening / closing device that transmits to D, and includes a fixing portion W (fixing the driven shaft), and an acting body A is provided on a driving support shaft P (provided at the end of the driving rotating body opposite to the driving shaft). One of the action support shaft (provided at the end opposite to the drive support shaft) of the action body and the drive shaft of the drive rotation body is attached to the fixed portion W, and the other is the driven rotation body D. In which one of the working support shaft and the drive shaft is provided at a position close to the driven shaft O, and the other is provided at a position far from the driven shaft O. A door stop that abuts against D and prevents rotation of one of the driven rotating bodies D, and Switchgear to the axial line and the axial line of the working body of the rotating body is approaching in a straight line to the driven rotary member, characterized in that for adhering per the door "

The “link device that connects the driven rotating body and the fixed portion with two rigid bodies” is obtained by removing the swing link from the link device that connects with the three rigid bodies, and the link device is provided by the presence of the swing link. The free movement of is impaired. Whether the shaft core line approaches a straight line when closed or the shaft core lines substantially overlap at the time of closing, the link device is required if the door itself does not distort in the direction toward the pivot axis O of the door (as shown in FIG. 103) before closing. Since the door does not move and closes while the door is distorted, the rotational resistance around the pivot axis O of the door is very large. That is, these devices have a feature of sealing while decelerating.
When the driven rotating body is brought into close contact with the door stop, the axial core line of the driving rotating body and the working body are aligned in a straight line regardless of whether the axial core line approaches a straight line or closes when closed. The former provides a compressive force and the latter provides a tensile force.

The axial force generated when these two axial core lines approach a straight line is generated when the two axial core lines are not in a straight line (and when the rotational radius of the circular motion of the drive support shaft P is long). Compared with the axial force, this device is “switching means”, and the “switching means” rotates the “action line of the force acting on the door” around the driving support shaft P. There is a big difference in size. It does not have the above-described releasable restraining means.
When the driven rotating body is brought into close contact with the door stop, the “line of action of the force acting on the door” is substantially perpendicular to the “closed door surface D0” in FIG. 64 is substantially parallel. However, the magnitude of the working force is sufficient to seal the door.

When the shaft cores of the two links almost overlap before closing, the action support shaft of the acting body revolves around the drive shaft, but the revolution of the action support shaft is restricted by the action support shaft attaching to the driven rotating body. Is done. If a swing link is inserted between the working support shaft and the driven rotating body and the drive shaft and the driven rotating body are connected by three links, the revolution of the working support shaft is not constrained.
As shown in FIGS. 13 and 38 to 40, the rotation of the “rotating drive body that is rotatably supported around the drive shaft” is driven (rotated about the driven shaft). An opening / closing device for transmitting to a body, including a fixing portion (fixing the driven shaft), and an operating body coupled to a driving support shaft (provided at an end opposite to the driving shaft) of the driving rotating body; A swing link is attached to the action support shaft (provided at the end opposite to the drive support shaft) of the action body, and the swing link (opposite to the drive support shaft or the action support shaft) is provided. One of the link support shaft (provided at the end on the side) and the drive shaft is attached to the fixed portion, and the other is attached to the driven rotating body, and the rotation of the driven rotating body causes the above-mentioned around the driving support shaft. A releasable restraining means for restraining the rotation of the acting body in one direction is provided. Equipment. "

50 and 65, the opening / closing device is provided with a releasable restraining means around the drive support shaft instead of the releasable restraining means attached around the link support shaft. In FIG. 66, the two rigid bodies are integrated. A swinging link is added to the rotating mechanism that rotates. It is a “means for switching the rotation radius of the action point”, and is an opening / closing device that operates on the lever principle only when sealed, as in FIGS. In FIG. 13, when the rotating body J and the link A are separated from each other, the operating point is the connecting shaft P, and the rotating radius of the operating point is large, and when the rotating body J and the link A are in contact, the operating point is the connecting shaft PP. The radius of rotation at the point of action is small.

Even if the force acting on the door is small, it is necessary to accelerate and decelerate just before closing because the force is applied. FIGS. 75 and 76 show that the “opening / closing device is a link device constituted by a link, and includes a connecting shaft in which the“ angle between adjacent links ”changes from increasing to decreasing or decreasing to increasing. An opening / closing apparatus comprising releasable restraining means for restraining rotation of the adjacent links around the door. 45 and 46 distribute the “force acting on the door” to the door and the door frame by sliding a part of the apparatus on the door frame, and FIG. 47 applies the force in the direction opposite to the rotation direction of the door. It works. By such means, the force acting on the door just before closing can be reduced.

61 and 63, the moving body is a rotating body (D) that is rotatably supported around a rotating shaft (O), and the door stop Gd that prevents rotation of one side of the rotating body D is the above-mentioned. Provided in the fixed part (W), the connection shaft (c) and the fixed support shaft (Sw) are connected by C two links (J, A), and the two links (J, A) are connected to the connection shaft ( P), which is connected to the rotating shaft (O), the connecting shaft (C), the fixed support shaft (Sw), and the connecting shaft (P).
The crossing angle (Θaj) of the axis lines of the two links (J, A) increases or decreases, approaching a straight line or overlapping state, and the rotating body (D) is brought to the door stop (Gd). 1 to 3 of the opening and closing device, which is characterized by pressing. The opening / closing device is a link device including links, and includes a connecting shaft that continuously increases or decreases the “angle between adjacent links”, and biases the rotation of the adjacent links around the connecting shaft. It is characterized by having a spring to perform. ''

In FIG. 61, “the drive rotator is just before the drive rotator comes into contact with the door stop while the distance between the working support shaft and the drive shaft is reduced as the drive rotator approaches the door stop. The axis of rotation of the actuating body approaches the state where the axis of the actuating body substantially overlaps, and the axis of rotation of the driving rotator and the axis of the actuating body substantially overlap with each other, and the rotating body of the drive rotates to rotate the driven rotation. An opening and closing device characterized in that a body is brought into close contact with the door stop.
In FIG. 63, the rotational force (M) acting around the center of rotation (C) is the product of the force (F) and the distance between the vector of force (F) and the center of rotation (C) (Lf). Since (Mc = Fb * Lbc), Lf decreases and F increases. Since ((Mo = Fb * Lbo)), Lb increases and Mo increases.

61, 62 and 63 are plan views for explaining the operation of the embodiment having the same structure as that shown in FIGS. 56 (b) and 56 (c), respectively. The support shaft Sw is connected by two links J and A to rotate the door D or the driven rotating body. In the case of FIG. 61 (a), the connecting point P of the two links is on the side of the rotating shaft of the two rotating bodies close to the pivot axis O of the door, and in FIG. 61 (b), the connecting point P of the two links is 2. It is outside the rotation axis of the two rotating bodies.
In FIGS. 61 (a), 62 (a), and 63, a torsion spring UV is charged around the connecting shaft in FIGS. 61 (b) and 62 (b), and rotated around the fixed support shaft Sw. The rotation of the body J in the direction of arrow B in the drawing is transmitted to the rotation of the door D in the direction of arrow A in the drawing.

In the process from when the door opening angle Θ is 90 degrees fully opened to when it closes to 0 degrees, the operation of the door D, the rotating body J, the link A, and the change of the position of the connecting shaft C and the position of the fixed support shaft Sw Is represented by a dotted line, and a state where the door opening angle is 10 degrees is represented by a solid line.
While the door opening angle Θ reaches a state represented by a solid line of 10 degrees from the fully opened state of 90 degrees, the connecting shaft C and the fixed support shaft Sw approach each other, and the link A and the rotating body J are placed with the connecting shaft P in the middle. From the open state to the closed state, after the state indicated by the solid line with the door opening angle of 10 degrees, the connecting shaft C and the fixed support shaft Sw are almost in the same position, and the link A and the rotating body J overlaps and rotates as a unit.
After the state represented by the solid line in which the door opening angle is 10 degrees, when the connecting shaft C and the fixed support shaft Sw are in the same position and the link A and the rotating body J have the same length, the link A and the rotating body J And rotate completely in an overlapping manner.

In FIG. 61 (a), the intersections between “the straight line Tswo passing through the door pivot O and the fixed support shaft Sw” and the circles Ro and Rsw are CC5 and PP5, respectively, and the distance between the points CC5 and PP5 is Lamax. Then, at least the length of the link A is Lamax or less, and if the position of the connecting shaft C is not far from the door pivot O and the fixed support shaft Sw, the connecting shaft C is closed and rotated in the direction of arrow B in the figure. While continuing to do so, the connecting shaft P does not revolve in the direction of arrow A in the figure. When the length of the link A is equal to or greater than Lamax and the connecting shaft C continues to rotate and close in the direction indicated by the arrow B in the drawing, the connecting shaft P at the tip of the link A is returned back on the circle Rsw in the direction indicated by the arrow A There is no. If the position of the connecting shaft C is close to the pivot O of the door and the fixed support shaft Sw, the connecting shaft C moves on the circle Ro along the arrow Ro in the drawing along with the revolution of the connecting shaft P in the direction indicated by arrow A in the drawing. Go back in the opposite direction.
As the fixed fulcrum Sw is closer to the pivot axis O of the door than the connection shaft C and the distance between the fixed support shaft Sw and the connection shaft C is smaller, the link device rotates more greatly before closing. When the fixed support shaft Sw is farther from the door pivot O than the connection shaft C, the door rotates in the opening direction just before closing.

61 and 62, when the center connecting shaft C of the rotation of the two links J and A is far from the fixed support shaft Sw, the shaft core lines Zj and Za of the two links J and A are bent in FIG. In other words, in the “range from fully open to immediately before closing (A)”, the torsion spring UV is less stretched and the connecting shaft P around the connecting shaft C is also less rotated. The “action line F of the force acting on the door” acts toward the vicinity of the door pivot O, not only keeps the force acting on the door small, but also increases the rotational resistance around the door pivot O to increase the rotational speed of the door. Is slowing down.
In FIG. 61 (a), the longer the rotating body J and the link A are, the closer the connecting shaft P approaches the pivot axis O of the door, and the position of the connecting shaft P is closer to the door pivot O and acts on the door. The distance between the line of force action and the pivot axis O of the door is reduced.

61 (a), 62 (a), and FIG. 63, the rotational force acting around the connection axis C is converted into the axial force acting around the fixed support shaft Sw in FIG. 61 (b). To do.
In FIGS. 61 and 62, the embodiment for converting the driving force of the bending moment acting around the connecting axis C into the pressing force is the embodiment of FIGS. FIGS. 40 and 46 show an embodiment in which the axial center line of the link A approaches a straight line and is substantially perpendicular to the closed door surface, and the magnitude of the axial force acting on the link A approaches infinity. 63B, 21, 49, and 50 are examples in which the axis J of the rotating body J and the link A approaches a straight line in FIG. 63 and the magnitude of the axial force acting on the link A approaches infinity.
In the “range from immediately before closing to the closing time (i)”, the center connection shaft C of the rotation of the links J and A in FIGS. 61 and 62 approaches the fixed support shaft Sw, and the two links J and A The shaft core lines Zj and Za shift from the straight line state to the bent state, and in FIG. 63, the bent state shifts to the straight line state. At this time, the torsion spring UV greatly expands and contracts, and the connecting shaft P is connected to the connecting shaft C. A large rotation around. The embodiment of FIGS. 61, 62, and 63 is characterized in that the two links rotate greatly at the end of the rotation of the door, and a large force suddenly acts on the door.
In any case, when sealed, the axis of the rotating body J and the link A approaches a straight line, and goes straight to the closed door surface. Further, the axial force acting on the rotating body J and the link A approaches infinity as the axis of the rotating body J and the link A approaches a straight line. In any case, when sealed, the rotational force close to zero is converted into an infinite axial force.

In FIG. 61 (a), the rotation of the link A around the connection axis C and the connection axis P do not change the rotational direction of rotation around the link A, and the “intersection angle Θad between the link A and the door surface” increases. Going further, the “intersection angle Θaj between the link A and the rotating body J” keeps decreasing. Therefore, in FIG. 61A, the torsion spring UV is charged around the connecting shaft C or the connecting shaft P. For the same reason, the torsion spring UV is charged around the fixed support shaft Sw or the connecting shaft P in FIGS. 61 (b) and 62 (b). In the case of FIG. 63, any link and the connecting shafts at both ends thereof rotate or move in one direction, so that the connecting shaft of any link is urged or moved by the pull spring V or the push spring U. The linking device operates and functions even when biased by the spring UV.

However, in the case of FIG. 62, since the direction of rotation or movement of the connecting shaft of any link is not one-way, the urging means may not be provided on the connecting shaft of any link.
In FIG. 62 (a), the “intersection angle Θjd between the rotating body J and the door surface” changes from decreasing to increasing before closing, so that when the torsion spring UV is charged around the fixed support shaft Sw, the door is moved before closing. Stop. In FIG. 62 (b), the “intersection angle Θad between the link A and the door surface” changes from decreasing to increasing before the closing dimension, so that when the torsion spring UV is charged around the connecting axis C, the door stops before the closing dimension. To do. In FIG. 62A, a torsion spring UV is charged around the connecting shaft and in FIG. 62B around the fixed support shaft Sw.

FIG. 61 shows an embodiment in which the connecting shaft P moves in a region closer to the door pivot O than the center of rotation, and FIG. 62 shows an embodiment in which the connecting shaft P moves in a region far from the door pivot O, and operates and functions in the same manner.
However, in FIG. 62 (a), unlike FIG. 61, the moving direction of the connecting shaft P changes noticeably immediately before closing. When the spring U is sandwiched between the link A or the rotating body J and the door surface, the link A or the rotating body J and the door surface come into contact with each other through the spring U just before closing, and the rotation of the link A or the rotating body J and the door The rotations interfere with each other and decelerate the door. The spring U is biased in the direction opposite to the rotation direction of the door just before closing, but is biased in the sealing direction when sealed.

In FIG. 61 (a), the action line F of the force acting on the door in the “range from fully open to just before closing (A)” is in the vicinity of the pivot axis O of the door and the action line F of the force acting on the door. The distance Lf between the door and the pivot O of the door decreases, but in the case shown in FIG. 61 (b), the distance Lf and the closing speed increase. Even if the door rotates with a small force in the range from fully open to just before closing, if it accelerates just before closing, the magnitude of the impact sound generated at closing will not be reduced. Further, when a large force suddenly acts on the door when the latch comes into contact with the door frame W, the door is sealed at once. For this reason, when the latch comes into contact with the door frame W, the “direction of the force acting on the door” is devised so as to be directed to the pivot axis O of the door as much as possible.
Immediately before closing, in the case of FIG. 61 (a), the direction of force is changed, and in the case of FIG. 62, the spring U is biased in the direction opposite to the closing direction, thereby making the distance Lf zero or negative. I can do it. Thus, even when the rotation is decelerated to a state close to stopping while the door is closed, if the mechanism described in FIGS. 3 to 5 is used as the spring mechanism for driving the link device, the door is opened slightly. It does not stay stopped even if you release your hand.
The embodiment shown in FIGS. 61 (a) and 62 does not use a resistor unlike a normal door closer, and can decelerate and seal strongly just before closing.

The deceleration immediately before closing will be described.
Similar to the embodiment of FIGS. 61 and 62, there is a structure in which a normal door closer also has a structure in which a door and a door frame are connected by two links, and the shaft cores of the two links overlap when sealed, As in the embodiment of 62, there is no feature that is substantially perpendicular to the door surface where the axis of the rotating body J and the link A is closed when sealed.
As in the present invention, within the range in which the force of the spring acts weakly to drive the closing device, in the embodiment shown in FIGS. 61 and 62, it is possible that the link axis passes through the vicinity of the pivot axis O of the door. The speed is greatly affected.
61-63 is a crank mechanism that converts a circular motion of one side into a linear motion of the other, and the crank mechanism includes two links of the rotating body J and the link A. It is difficult to operate when the axis lines are in a straight line and when they are overlapped, and it is easy to operate when the angle between the two links is close to a right angle. Unlike the normal door closer, when the spring force is weak and acts on the closing device as in the present invention, the crank mechanism is Decelerate to near stop.

In FIG. 61 (a), the connecting shaft C moves on a circumference Ro centered on the pivot axis O of the door, and the connecting shaft P moves on a circumference Rsw centered on the fixed support shaft Sw. The circular trajectory Rc is the trajectory of the connecting axis P centered on the connecting axis C, and the intersection angle between the circular trajectory Rc and the circumference Rsw is large in the “range from fully open to immediately before closing (A)”. It becomes smaller in the “range from just before closing to the time of closing (i)”. As it approaches at the time of closing, it approaches the circular orbit Rc and the circumference Rsw, and the rotating body J and the link A try to rotate in a state close to unity.
When the angle between the shaft cores of the two links of the rotating body J and the link A is large, the connecting shaft C is easy to move and the connecting shaft P is difficult to move, and when the angle is small, the connecting shaft P is easy to move. C is difficult to move. When the rotating body J and the link A approach one, the connecting shaft P moves without the connecting shaft C moving, and an axial force acts on the link A.

The arc Rsw shown in FIGS. 61 (a) and 61 (b) is centered on the fixed support shaft Sw, and the arc Rc10 is a circumference centered on the connecting shaft C10. The arc Rsw and the fixed support shown in FIG. 61 (b) are shown. The distance δc between the axes Sw represents a change in the distance between the connection axis C and the fixed support shaft Sw.
Assuming that the state in which the latch is in contact with the door frame W is in a state D10 indicated by a solid line, assuming that the link continues to rotate while the rotation of the door is stopped, the rotating body J and the link A correspond to the distance δc. An axial force is generated by the strain that is generated, and the magnitude of the axial force increases as the link rotates, and grows to a size that seals the door.

Link even if the rotation of the door stops depending on whether the position of the connecting shaft C or the fixed support shaft Sw moves, the length of the rotating body J or the link A changes, or the door is distorted in the radial direction of the circular motion. Can continue to rotate. In FIG. 61 (a), the door is distorted in the direction in which the door is pulled away from the door pivot. In FIG. 61 (b), the door is distorted in the direction in which the door is pulled away from the door pivot.
In FIG. 61 (a) and FIG. 61 (b), a tensile force acts on the rotating body J or the link A connected to the connecting shaft C, and the tensile force is latched when the latch contacts the door frame W at the beginning. Even if there is no force to dent, it grows gradually until it gets close to the door. At the same time, the pulling force acting on the link A increases the rotational resistance acting around the rotation axis of the door, so the door closes while decelerating. When the force acting on the door is set to be small, the rotational resistance acting around the rotation axis of the door is a large factor that changes the closing speed of the door.

When the door is distorted in the direction of being pulled toward the door pivot, the distance between the door side and the door frame is widened on the latch side, and the latch is easily recessed.When the door is distorted in the direction of being pulled away from the door pivot, the distance is Narrows and latch becomes difficult to dent. When the force acting on the door is set small, the resistance of the latch plays a large role just before the door closes, and the `` force acting in the radial direction of the circular motion of the door '' is not related to the rotation of the door. In addition, the door closing speed is reduced by performing a task different from the rotation of the door. Thus, the “elapsed time from when the latch contacts the door frame W until the door comes into close contact with the door stop” is extended, and thereafter “the force acting in the circumferential direction of the circular motion of the door” gradually increases. Thus, the impact sound generated at the time of closing is relieved.

In the embodiment of FIG. 63, as in the embodiment of FIG. 61, the axial force acting on the rotating body J and the link A approaches infinity as the axial cores of the rotating body J and the link A approach a straight line. 61, the connecting point P between the rotating body J and the link A is outside the rotating shafts of the rotating body J and the link A in FIG. 61, and the tensile force acting on the rotating shaft Q of the rotating body J acts on the link. In FIG. 63, the connecting point P of the two links is in the middle of the rotational axis of the rotating body J and the link A, and the rotational force acting on the rotational axis Q of the rotating body J is converted into the compressive force acting on the link. .

FIG. 63 utilizes the buckling phenomenon of the compression material. Compressed material supports a large compressive force when it is stretched, but it becomes extremely weak in the Gulf. 63 (b) to (c), when the rotating body J and the link A are stretched from the bent state at the connecting shaft P, the connecting shafts C at both ends of the connecting member composed of the rotating body J and the link A are connected. The fixed support shaft Sw will transmit a large compressive force to the rotation of the door.
When the compression material is compressed and the length of the compression material is reduced, the compression material is buckled by being slightly reduced in length, and then the linear distance between both ends of the compression material is greatly reduced. 63 (b) to 63 (c), the linear distance between the connection shaft C and the fixed support shaft Sw is slightly increased, so that the rotating body J and the link A are stretched from the state where the connection shaft P is bent. . That is, the rotating body J and the link A are stretched while the door is slightly rotated just before sealing, and suddenly a large force is transmitted to the door.

In FIG. 63 (a), the connecting shaft C moves on the circumference Ro centered on the pivot axis O of the door, and the connecting shaft P moves on the circumference Rsw centered on the fixed support shaft Sw. The circle Rwc is a circle having a radius between the position C0 of the connecting shaft C when sealed and the position of the connecting shaft C when sealed around the fixed support shaft Sw.
The circle Rwc is outside the circumference Ro, and as the sealed door is opened, the connecting shaft C moves to the inside of the circumference Ro and leaves the circle Rwc. This is because the distance between the connecting shaft C and the fixed support shaft Sw decreases as the sealed door is opened, and the intersection angle Θaj between the shaft core line Zj of the rotating body J and the shaft core line Za of the link A is sealed. It will continue to increase as the door is opened. Therefore, if the axial center line Zj of the rotating body J and the axial center line Za of the link A are set to be bent slightly from a straight line when sealed, the state shifts to a bent state as the sealed door is opened.

The bent state becomes more prominent as the length of the link A with respect to the rotating body J is shorter. In FIG. 63 (a), the distance between the circle Rwc and the circumference Ro is zero at the position of the intersection C0, and increases rapidly near the position of C0 as the sealed door is opened, and then becomes constant. This means that the axis core line Zj of the rotating body J and the axis core line Za of the link A are bent in the “range from fully open to just before closing (A)”. It means that it will be in a straight line in the “range”. From the fully open position to the closed position, the “intersection angle Θaj between the axis center line Zj of the rotating body J and the axis center line Za of the link A” increases slightly during sealing while slightly increasing.
This sudden change becomes more prominent as the position of the fixed support shaft Sw moves away from the door pivot O to the handle side.

Just by setting the fixed support shaft Sw to the handle side from the pivot O of the door and setting the shaft core line Zj of the rotating body J and the shaft core line Za of the link A to be slightly bent from a straight line when sealed, immediately before closing. Suddenly, a large sealing force appears. Since the bent state is not reversed halfway, even if the side to be bent is the door side as shown in FIG. 63 or the opposite side. Only the urging direction around the connecting axis C is reversed. The sealing force is generated when the door abuts against a door stop (not shown) and rotation is prevented.
In FIG. 63 (a), a straight line T is a straight line passing through the pivot axis O of the door and the fixed support shaft Sw, and a circle Rswb is a circle in contact with the circumference Ro around the fixed support shaft Sw. The distance between the circle Rswb and the circumference Ro is zero at the position of the intersection C70, and the “distance between the fixed support shaft Sw and the connecting shaft C” indicates a local minimum value, and the position of the C70. It turns from decrease to increase. That is, the door D stops at the position C70.

The arc Rsw shown in FIG. 63 (c) is centered on the fixed support shaft Sw and the arc Rc5 is a circumference centered on the connection shaft C5, and the distance δcq between the arc Rsw and the arc Rc5 is the connection shaft C and the fixed support point. It represents the change in distance between Sw. The shape of the region between the arc Rsw and the arc Rc5 is a concave lens shape in the case of FIG. 61 and a convex lens shape in the case of FIG.
The change in the distance δcq between the arc Rsw and the arc Rc5 due to the rotation of the link device in FIG. 63 is half of that in FIG. 61, and “the force acting on the door after the latch contacts the door frame W” The “increase rate” is greater in the case of FIG. 63 than in the case of FIG. Therefore, in the case of FIG. 63, the rotation of the door is more likely to stop when the latch contacts the door frame W than in the case of FIG.

The connecting shaft C is provided on a rotating body Jc that rotates about a rotation support shaft Ij provided on the door D, and a pressing spring U is mounted between the rotating body Jc and the door. FIG. 63 (b) shows a state D5 when the latch is in contact with the door frame W. After that, the axial force is generated in the rotating body J and the link A as the axial cores of the rotating body J and the link A approach a straight line. The push spring U contracts and the connecting shaft C moves in a direction approaching the door surface.
When the rotation of the link device is directly transmitted to the rotation of the door, the link device can continue to rotate when the rotation of the door stops. In the case of FIG. 61, the link device that has stopped rotating due to the stop of the rotation of the door moves in the radial direction of the circular movement, and in FIG. 63, the position of the connecting shaft C moves. This makes the link device easier to rotate. When the link continues to rotate, in the case of FIG. 61, the door further moves in the radial direction of the circular motion, and in FIG. 63, the position of the connecting shaft C further moves, and the link device becomes easier to rotate.

Initially, the axial force generated on the rotating body J and the link A does not cause the latch to be depressed, and the axial force increases with the rotation of the link. Grows to seal the door. That is, the “range from fully open to just before closing (A)” ends. At the same time, a strong force suddenly appears and the door does not collide with the door stop. Even when there is no force to make close contact with the door stop, the rotation of the link device does not stop, and the sealing force is gradually grown. Thus, time elapses immediately before closing until sealing.
The push spring U inserted between the rotating body Jc and the door does not act as an external force that opposes the force acting on the door, but the expansion and contraction of the spring acts as an internal force that works in the direction of closing the door. Accordingly, the push spring U does not reduce the force of the spring that rotates the door in the closing direction like the spring provided in Patent Document 12.
The expansion and contraction of the two springs, the push spring U and the torsion spring UV of the drive unit, means that the expansion and contraction of the spring increases with a slight rotation of the door, and the rigidity of the spring decreases.

FIG. 64 is the same structure as FIG. 63, and is a link device in which a door and a door frame are connected by two links. When closed, the shaft cores of the two links approach a straight line and convert a small rotational force into a large compressive force. This is an example. The mounting shaft close to the pivot axis O of the door does not move, and the “distance Lf between the force action line F and the center of rotation” does not increase.
Since the two links are closed and rotated by the compression force, the fixed support shaft Sw and the connection shaft C, which are the mounting shafts of the two links, are moved away from each other.
The straight line Ts is a straight line passing through the door pivot O and the fixed support shaft Sw, and is a boundary line where the urging direction is switched. When the door is on the fully open side with respect to the straight line Ts, it is biased in the opening direction, and when the door is on the closing side, it is biased in the closing direction. In addition, the angle between the two adjacent links around the connecting axis P changes from increasing to decreasing, or from decreasing to increasing.

64 (a) and 64 (b), the connecting shaft C is attached to a position far from the pivot of the door, and the rotation of the drive rotator is opposite to each other in FIGS. 64 (a) and 64 (b).
64A shows a case where the shorter link is attached to the connection axis C, and FIG. 64B shows a case where the longer link is attached to the connection axis C. FIG.
The biasing means around the mounting shaft must be rotated in a direction that provides a compressive force to the link. In FIG. 64 (a), in the spring loaded around the fixed support shaft Sw, the direction in which the compression force is applied to the link and the rotation direction of the link are different. Therefore, a spring cannot be charged around the fixed support shaft Sw. The urging direction and the rotation direction of the link are the same around the connection axis C, and the rotation direction of the link does not change midway. Therefore, a spring is charged around the connection axis C.
In FIG. 64B, the urging direction and the rotation direction of the link are the same around the fixed support shaft Sw and the connection axis C, but the door is fully opened around the connection axis C with the straight line Ts as a boundary. The rotation direction of the link changes depending on whether the door is on the side or the door is on the closing side. Therefore. Therefore, a spring is charged around the fixed support shaft Sw.

64 (c) and 64 (d) are provided with a connecting shaft C at a position close to the pivot of the door, and the link attached to the connecting shaft C is short in FIG. 64 (c) and long in FIG. 64 (d).
In both FIG. 64C and FIG. 64D, the angle between two adjacent links around the connecting axis C changes from increasing to decreasing, or from decreasing to increasing. Therefore, a spring is charged around the fixed support shaft Sw.
Either one is the drive rotator and the other is the working body, but the urging direction is the same as the rotation direction of the link, and the rotation direction of the link changes with the mounting shaft that loads the ring spring of the urging means There is no mounting shaft on either one. The angle between two adjacent links continues to increase or decrease

FIG. 65 shows an opening / closing device that transmits the rotation of the driving rotator J in the direction indicated by the arrow A to the driven rotating body D and rotates the driven rotating body D around the driven rotating body rotation axis O in the direction indicated by the arrow B in FIG. Thus, it is a link device that connects the driven rotating body D and the fixed support shaft Sw of the fixed portion with three links. In the figure, the working body A is provided with a working support shaft PP at one end and a driving support shaft P at the other end, and the working body A is connected to the driving rotating body J by the driving support shaft P. The link AA is connected to the operation support shaft PP. FIGS. 65 (a) and 65 (b) show a case where the rotary shaft of the drive rotator is attached to the fixed support shaft Sw of the fixed portion and the link AA is supported by the connecting shaft C, and FIGS. The case where the body rotation shaft is attached to the connection shaft C and the link AA is pivotally supported by the fixed support shaft Sw of the fixed portion is shown.

In FIGS. 65 (a) and 65 (b), a torsion spring UV is attached around the fixed support shaft Sw, and the rotating body J is urged in the direction of arrow A in the figure, and a tensile force acts on the acting body A and the link AA. In FIGS. 65 (c) and 65 (d), a torsion spring UV is attached around the connection axis C, and the rotating body J is urged in the direction of arrow A in the figure, and a compressive force acts on the acting body A and the link AA. The hits G1 and G2 are in contact with the link AA to prevent the rotation of the link AA in the direction opposite to the arrow C in the figure and the rotation of the link AA in the direction of the arrow C in the figure.
The contact G1 abuts on the link AA and keeps the position of the action support shaft PP in the vicinity of the pivot axis O of the door within the “range (A)”. The link AA is separated from the contact G1 just before closing, rotates in the direction of the arrow C in the figure, contacts the contact G, and moves the position of the action support shaft PP away from the door pivot axis O in the “range (ii)”. .

65 (a) and 65 (c) show the middle of the closing process with a broken line, the solid line shows the state just before closing, and the state immediately after the axis core line Za of the acting body A crosses the center of rotation of the link AA, The beginning of the “switching means” is shown. In FIG. 65 (c), Za120 indicated by a broken line passes over the driven body D and urges the driven body D in the direction opposite to the arrow B in the figure. That is, the door is urged in the opening direction, and the door is pressed against the “door opening in the opening direction (not shown)” to be stationary. When the position of the fixed support shaft Sw is moved and the stop position of the working support shaft PP is moved in the direction of the arrow X in the figure, the door opening angle Θd that changes from the closing direction to the opening direction becomes smaller.

65 (b) and 65 (d), the solid line indicates the closed state, and the middle of the process of opening the closed door is indicated by the broken line. An axis core line Za of the acting body A indicated by a broken line indicates a state immediately after crossing the center of rotation of the link AA again, that is, an initial state returning to “rotating means in the range (A)”. In FIG. 65 (b), the door opening angle Θd when returning to the “rotating means in the range (A)” in the opening process is the door opening angle Θd when switching to the “rotating means in the range (I)” in the closing process. Larger than the opening angle Θd.
In the closed state shown by the solid lines in FIGS. 65 (b) and 65 (d), the axial force acting on the acting body A becomes infinite as the axial cores of the acting body A and the rotating body J are positioned on a straight line. Approaching large.
Za120 indicated by a broken line passes over the driven body D and urges the driven body D in the direction opposite to the arrow B in the figure. That is, the door is urged in the opening direction, and the door is pressed against the “door opening in the opening direction (not shown)” to be stationary. When the position of the fixed support shaft Sw is moved and the stop position of the working support shaft PP is moved in the direction of the arrow X in the figure, the door opening angle Θ that changes from the closing direction to the opening direction becomes smaller.

FIG. 66 illustrates a sealing mechanism that seals while applying resistance to the rotation of the door. Since the resistance disappears at the time of sealing, the force of the spring does not need to be more than the force necessary to seal the door. . Even if the door does not accelerate at the same speed in the range (A), if the spring force is switched to act strongly on the door immediately before closing, the door will accelerate even in a slight rotation in the range (A). Makes an impact sound. In such a case, the sealing device must have a function of sealing while applying a brake. In addition, even when the door is accelerated by the force of the sealing of the door in the “range from fully open to just before closing (A)”, the impact sound is not generated if the door is accelerated while applying the brake.

The structure and operation of FIG. 66 will be described.
FIG. 66 is a plan view for explaining the operation of the link device for connecting the fixed support shaft Sw provided on the door frame W and the connection shaft C provided on the door with two links (rotating body J and link A) as in FIGS. In this case, G1 and G2 are attached to each of the rotating body J and the link A, and the rotation of the link around the connecting axis P of the link A and the rotating body J is constrained when G1 and G2 contact each other before the closing dimension. To do. As in FIG. 13, the link A and the rotating body J are integrated, and the rotating body J and the door continue to rotate.
When the two links connecting the fixed support shaft Sw and the connecting shaft C are integrated, they cannot be rotated, but in FIG. Similarly, a push spring U is interposed between the contact G1 and G2 so as to be rotatable. At the same time, it is decelerated by the expansion and contraction of the spring just before closing.

A torsion spring UV is attached around the connection axis P of the link A and the rotating body J, and a spring (not shown) that operates only at the time of sealing described with reference to FIGS. The torsion spring UV causes the link A and the rotating body J to rotate in the direction of closing around the connecting shaft P, the rotating body J rotates around the fixed support shaft Sw in the direction indicated by arrow A, and the door D is indicated by the arrow in the figure. Close and rotate in the B direction.
The link A rotates around the connection axis C by the biasing force of the torsion spring UV. When the link A reaches a predetermined rotation angle, a spring that is attached around the connection axis C and that operates only when sealed is provided. Start working and rotate link A instead of torsion spring UV.

FIG. 66 (a) shows the time when fully opened by a solid line, and shows the operation in the “range from the time when fully opened until just before closing (A)” by a dotted line. In the range (A), the connecting shaft C moves largely on the circle Ro centered on the door pivot O, but the connecting shaft P moves slightly on the circle Rsw centered on the fixed support shaft Sw to pull the connecting shaft C. . The closer the connecting shaft P is to the pivot axis O of the door, the more the connecting shaft P stays in the vicinity of O. However, the longer the length of the link A and the rotating body J is, the closer the radius of the circle Ro is. Stays close to the pivot axis O of the door.
Further, at the end of the range (A) when the link A rotates, the link A is substantially parallel to the door surface, and the direction of the “force pulling the connecting shaft C” is directed to the door pivot O. The force acting on the door pivot O not only does not rotate the door, but also increases the rotational resistance of the door pivot O to decelerate the door.

66 does not have a torsion spring UV attached around the connecting shaft P, and is attached around a spring (not shown) or a connecting shaft C that is urged around the fixed support shaft Sw in the direction of arrow A in the figure. It operates by attaching a spring (not shown) that biases in the direction of the middle arrow c.
When a spring urging around the fixed support shaft Sw is attached in the direction of arrow A in the figure, the range between the fully open position C90 and the moved position C70 where the door is slightly closed is the spring in the direction to open the door. Therefore, the link A and the rotating body J are in a straight line and are stationary when fully opened.
FIG. 66 (b) shows the time when fully closed by a solid line, and shows the operation in the “range from right before closing to the time of closing (i)” by a dotted line. In the range (i), the magnitude of movement of the connecting axis C on the circle Ro is small, and the connecting axis P moves largely on the circle Rsw. In this case as well, the lengths of the link A and the rotating body J are approximated, and the closer the connecting shaft C is to the fixed support shaft Sw, the closer to the radius of the circle Ro, the less the connecting shaft C moves.
At the beginning of the range (i), the hits G1 and G2 come into contact with each other so that the link A and the rotating body J are integrated. Since the length of the link A is larger than the length of the rotating body J, the link device becomes “a lever with the fixed support shaft Sw as a fulcrum, the connection shaft P as a force point, and the connection shaft C as an action point”. The door is strongly pressed against the door stop Gd.

In order to make the length of the link A larger than the length of the rotating body J so that the link device of FIG. 66 performs the above-described operation, the position of the fixed support shaft Sw is close to the pivot axis O of the door in the circle Ro. It must be within the range and farther from the “closed door surface D0” than the connecting shaft C when fully closed.
If the position of the fixed support shaft Sw and the connecting shaft C are sufficiently separated when fully closed, the distance between the fixed support shaft Sw and the connecting shaft C changes from decreasing to increasing before the closing, and the diagram of FIG. 66 (b). As shown in the middle Θ10, the crossing angle Θ between the link A around the connection axis P and the rotating body J is minimum. That is, at the beginning of the range (i), the crossing angle Θ is minimized. The force of the pressing spring U is maximum at the beginning of the range (Yes) and becomes zero at the end of the range (Yes). The force that constrains the rotation of the link device and decelerates the rotation of the door suddenly appears just before closing, and disappears on the map. In the figure, A10 is substantially perpendicular to the door surface, and A0 in the figure is substantially parallel to the door surface. The force of the push spring U decelerates toward the door pivot O immediately before closing, and acts in a direction perpendicular to the door surface during sealing to change to sealing force.

FIG. 67 shows an embodiment in which an urging means is mounted around a fixed support shaft Sw that is a drive shaft. In FIGS. The torsion spring UV2 is "rotating means in the range (ii)". In the “(A) range”, since the rotation of the driven rotating body is large and the rotation of the driving rotating body is small, the rigidity of the torsion spring UV2 is set large and the expansion and contraction is small. In the “(ii) range”, the rotation of the driven rotating body is small and the rotation of the driving rotating body is large, so the rigidity of the torsion spring UV1 is small and the expansion and contraction is large.
67 (a) is a fully open state, FIG. 67 (b) is a state diagram in the middle of closing, and FIG. 67 (c) is a state diagram in the closed state.

The rotating bodies J1 and J2 have the same rotating shaft and are rotatably supported around the fixed supporting shaft Sw. One end of the torsion spring UV1 is attached to the rotating body J1, and one end of the torsion spring UV2 is Attach to rotating body J2. The other end of the torsion spring UV1 is a spring support shaft S1 provided on the door frame W, and the other end of the torsion spring UV2 is a spring support shaft S2 provided on the rotating body J1.
In the state where the spring is most relaxed as shown in FIG. 67 (c), the rotating body J1 comes into contact with the contact G1 provided on the rotating body J2, and the rotation of the rotating body J1 in the direction of arrow A in the figure is prevented. The rotating body J2 contacts the contact G2 where the door frame W is provided, and is prevented from rotating in the direction indicated by the arrow B in the figure.

As shown in FIG. 67 (b), when the rotating body J2 is rotated in the direction of the arrow a in the figure, the torsion spring UV2 has a large rigidity so that it hardly expands and contracts, and the rotating body J1 hits and slightly separates from G1. The torsion spring UV1 greatly expands and contracts by rotating greatly until the rotating body J1 comes into contact with “the contact G11 where the door frame W is provided”. The process in which the rotating bodies J1 and J2 rotate in the direction indicated by the arrow B in FIG. 67 (b) to FIG. 67 (c) is a process in which the door is closed by the force of the spring. "Rotation". Since the torsion spring UV1 is greatly deformed with a small force, the small force of the torsion spring UV1 has almost no force to expand and contract the torsion spring UV2, and the torsion spring UV1 rotates with the force of only the torsion spring UV1 having a larger rigidity. .

When the rotating body J1 comes into contact with G11 and further rotates in the direction of arrow A in the figure, only the rotating body J2 rotates while the rotating body J1 is stopped, and only the torsion spring UV2 expands and contracts without expanding and contracting the torsion spring UV1. To do. The process of rotating the rotating bodies J1 and 2 in the direction of arrow B in FIG. 67 and moving from FIG. 67 (a) to FIG. 67 (b) is the process of closing the door by the force of the spring. "Rotation". After only the torsion spring UV2 expands and contracts, the torsion spring UV1 expands and contracts.

67 (a), (b), and (c), when the closed door is slightly opened, each of the springs having different rigidity expands and contracts from the weakly rigid torsion spring UV1, and each of the divided doors has a different rigidity. Does not work unaffected. 67 (d), (e), and (f) are embodiments in which each operates independently without being influenced by the other in the rotation range of separate doors divided by springs having different rigidity. Similarly to 67 (a), (b) and (c), the urging means U1 and U2 are mounted around the drive shaft fixed support shaft Sw. The biasing means U1 and U2 are elastic bodies shaped into U shapes and are springs U1 and U2. FIG. 67 (d) shows a state where the spring has returned to its natural shape. FIG. 67 (d) is a state diagram at the time of closing, FIG. 67 (e) is a state diagram during the closing, and FIG. 67 (f) is a state diagram at the time of full opening.
67 (d), (e), and (f), the spring U1 has a large rigidity and small expansion / contraction, and is "rotating means in the range (A)", and the spring U2 has a small rigidity and large expansion / contraction. “Rotating means in the range of (i)”.

The rotating body J is rotatably supported around the fixed support shaft Sw, and springs U1 and U2 are attached to the rotating body J. The slider S1 is attached to one side of the spring U1, and the slider S1 is housed in a groove H1 provided in the rotating body J and swings between the start end HS1 and the end HE1 of the groove H1. The other end of the spring U1 is attached to a spring support shaft Sv1 provided on the door frame W.
When the rotating body J rotates in either the direction of the arrow A or B in the drawing from the state where the spring shown in FIG. 67 (d) is most relaxed, the slider S1 keeps in contact with the terminal end HE1 of the groove H1 at the beginning of rotation. Further, the rotating body J rotates, moves away from the terminal end HE1, moves along the groove H1, and reaches the starting end HS1. The end HE1 is located far from the fixed support shaft Sw, and when the slider S1 is in contact with the end HE1, the force for rotating the rotating body J is strong. When the start end HS1 is close to the fixed support shaft Sw and the slider S1 is in contact with the start end HS1, the force for rotating the rotating body J is weak. If the starting end HS1 is at the position of the fixed support shaft Sw, the force for rotating the rotating body J is zero when the slider S1 is in contact with the starting end HS1.

Such an action of the spring U1 is that when the rotary body J is rotated in the direction opposite to the arrow A in FIG. The force for rotating J is the same as that acting weakly from the strong state, and the link S2 comes into contact from the state separated from the rotating body rotation axis Q, and the fulcrum of the pulling spring V2 is pulled to coincide with the rotating body rotation axis Q. The force by which the spring V2 rotates the rotating body J is the same as when the force is changed from the strong working state to the non-working state.
In FIG. 29, when the rotating body J is rotated in the direction opposite to the arrow a in the figure, the link S comes into contact with the rotating body Q from the rotating body rotating shaft Q, and the fulcrum Sv of the pulling spring V is brought into contact with the rotating body rotating shaft Q This is the same as the state in which the force that causes the pulling spring V to rotate the rotating body J does not work.

67 (d), (e), and (f), a slider S2 is attached to one side of the spring U2, and the slider S2 is accommodated in a groove H2 provided in the door frame W and is interposed between the start end HS2 and the end HE2 of the groove H2. Swing. The other end of the spring U2 is attached to a spring support shaft Sv2 provided on the rotating body J.
In the state where the spring shown in FIG. 67 (d) is most relaxed, the slider S2 is in the middle portion between the start end HS2 and the end HE2 of the groove H2, and the rotating body J rotates in either the direction of arrow A or B in the figure. At the beginning of the rotation, the slider S2 is kept in a state where it does not come into contact with the start end HS2 or the end HE2 of the groove H2, and the force by which the spring U2 rotates the rotating body J does not work. An example of the shape of the groove H2 in the drawing is an arc shape with the rotating body rotation axis Q as the center.
Further, the rotating body J rotates and moves along the groove H1, and reaches the start end HS2 or the end HE2. When the rotating body J further rotates while being in contact with the starting end HS2 or the terminal end HE2, the spring U2 changes from a state where the force for rotating the rotating body J does not work.
Such an action of the spring U2 is separated from the state in which the link S is in contact with the rotating body rotation axis Q in FIG. 29, and the pulling spring V is moved from the state where the force for rotating the rotating body J does not work. It is the same as becoming.

As shown in FIG. 67 (d), when the state is changed from the state where the spring U2 is loosened to the state where the force is stored in the spring shown in FIG. 67 (f), the door is opened, and the door is closed. This is a time when the state shown in FIG. 67 (f) where the force is stored shifts to the state shown in FIG. 67 (d) where the spring is loosened.
In the process of closing the door, when the spring U2 is loosened from the state shown in FIG. 67 (f) and the slider S2 leaves the start end HS2 or the end end HE2 of the groove H2 as shown in FIG. 67 (e), the position of the fixed support shaft Sw is reached. When the slider S1 is moved away from the starting end HS1, the rotating body J rotated by the spring U2 is rotated by the spring U1.
The opening degree of the door when the slider S1 moves away from the starting end HS1 after the force is stored in the spring U1 in the process of closing the door is the slider opening force from the state in which the spring U1 is loosened in the process of opening the door. The opening degree of the door when S1 leaves the terminal HE1 is different, and the opening degree of the door when the slider S1 leaves the starting end HS1 in the process of closing the door is the door opening degree when the slider S1 leaves the terminal HE2 in the process of opening the door. Smaller than the opening.

The other end of the springs U1 and U2 is a spring support shaft S2 provided on the rotating body J1.
In the state where the spring is most relaxed as shown in FIG. 67 (c), the rotating body J1 comes into contact with the contact G1 where the rotating body J is provided, and the rotation in the direction of arrow A in the figure is prevented. The rotating body J2 abuts against the contact G2 where the door frame W is provided, and is prevented from rotating in the direction indicated by the arrow B in this way. FIGS. 67 (d), (e), and (f) are shown in FIGS. Similarly to the spring mechanism described in 28 to 33, the rotating body is urged with different strengths of different sizes in the rotation range distinguished by the rotating body. 67 (d), (e) and (f), unlike FIGS. 3 and 4 and FIGS.

FIG. 68 is an urging means in place of the tension spring V and is provided with a path through which the action body linearly reciprocates. “Rotating means in the range (A)”, “Rotating means in the range (I)” and “Switching means” Is provided. If only this urging means is attached to the door and the rotational force acting on the door is the same as when other closing devices are attached to the door, the door performs the same operation. Therefore, the door provided with only this biasing means is the simplest and exhibits the same effect.

The passage body SZ includes a passage in which the action body A linearly reciprocates, and an end portion of the passage body SZ is attached to the fixed support shaft Sw. The action body A is inserted into a through hole H provided in the passage body SZ and attached to the passage body SZ so as to be movable in the axial direction.
One end of the tension spring V1 is attached to a spring support shaft provided in the passage body SZ, and the other end is attached to the acting body A through a through bolt Va. The through bolt Va is inserted into a through hole H provided in the working body A and attached to the working body A so as to be movable in the axial direction. The through bolt Va is separated from the contact Ga attached to the operating body A in the “(A) range”, and abuts on the through bolt Va to transmit the spring force to the operating body A in the “(A) range”. The through bolt Va is prevented from being transmitted to the acting body A by being separated from or contacting the contact bolt Va, or is transmitted.

Wheels B are mounted on the action body A, and sliding surfaces K1, K2 that move along the wheels B are attached to the passage body SZ via the sliding body KK. One end of the sliding body KK is rotatably supported around a connecting shaft P provided in the passage body SZ, and the other end is urged by a pulling spring V in a direction of pressing the wheel B. The sliding body KK includes sliding surfaces K1 and K2, and as shown in FIG. 68 (a), when the wheel B moves along K2, the “force Fb that the wheel presses the sliding surface” Move in the direction of arrow a in the figure. As shown in FIG. 68 (b), when the wheel B moves along K 1, “the force Fb that the wheel presses the sliding surface” works at right angles to the moving direction of the acting body A and does not move the acting body A.

FIG. 68 (a) shows a state in which the action body A is inserted most deeply into the passage body SZ, and FIG. 68 (b) shows a state in which the action body A is most separated from the passage body SZ.
FIG. 68 (b) shows “rotating means in the range (A)”, and the through bolt Va contacts the contact Ga, and the pulling spring V1 can urge the acting body A in the direction of arrow A in the figure. Since the wheel B moves along K1, the tension spring V2 works ineffectively.
FIG. 68 (a) shows “rotating means in the range of (i)”, and the wheel B moves along K2, and the tension spring V2 urges the acting body A in the direction of arrow A in the figure. The pulling spring V1 works ineffectively when the through bolt Va hits and moves away from Ga.

FIG. 69 is an explanatory diagram of a mechanism for braking the inertial force attached to the door. 69 (a) to 69 (c) use the reciprocating motion of the piston moving in the cylinder as the urging means, and the switching devices of FIGS. 69 (d) to 69 (f) are as shown in FIG. 1 (d). The urging means (not shown) is provided, and the urging means is provided so that the spring force does not act on the door as the door is opened.
69 (a) to 69 (c) is an urging means for connecting the door and the door frame, and the structure of the urging means is “the action body A is linearly reciprocated in the groove Jh by the pressing spring U”. It is intended to move, and is not urged to rotate like the link A in FIG. 6, but moves the link A in the axial direction as shown in FIG.
6 and 7, one of the connecting shafts of the door and the opening / closing device is provided in the vicinity of the pivot of the door, and the connecting shaft moves in a direction perpendicular to the “closed door surface”. A feature is that a passage perpendicular to the “closed door surface” is provided in the vicinity of the pivot of the door.

The structure and operation will be described with reference to FIGS. 69 (a) to 69 (c).
69 (a) to 69 (c) reduces the force of the spring by stopping the wheel B at a position very close to the pivot axis O of the door, and also has a large force sufficient to seal the spring. Regardless, by rotating with a very small force, the ratio of rotational force and sealing force is infinite.
That is, by making the distance between the axis A Za5 of the link A and the pivot O of the door as close as possible to zero, even if the distance between the axis A Za5 and Za0 of the link A is small, the spring is sufficiently sealed. You can have a lot of power.
In this manner, the opening / closing device shown in FIGS. 69A to 69C is housed in an elongate case along the door surface without protruding forward from the door surface, thereby realizing downsizing of the device.

A wheel B is mounted on a rotating shaft Ib of a wheel provided at the tip of the acting body A, and a sliding surface K that moves along the wheel B is fixed to a fixing portion that fixes the pivot O of the door. The groove body Jh is rotatably supported around the connection axis C, and includes a groove for moving the action body A along the axial direction. A push spring U is inserted between the groove body Jh and the action body A, The acting body A is urged so as to press the sliding surface K.
FIG. 69 (a) is a plan view for explaining the operation in the closing process from the time of full opening to just before closing, and FIG. 69 (b) is a plan view for explaining the operation in the process of opening the door from the time of closing.

The wheel B which is on the sliding surface K and presses the sliding surface K moves toward the side where the angle at which the axial center line Za of the link A intersects the sliding surface K is an obtuse angle. As shown in FIG. 69 (a), the “range from fully open to just before closing (A)” tries to move in a direction approaching the door pivot axis O, but the sliding surface K in the figure is on the pivot axis O of the door. It is blocked by a recess on the near side.
As shown in FIG. 69 (b), the circle Rc5 is the locus of the rotation axis Ib of the wheel B around the connecting shaft position C5 just before closing, and the straight line Zc5 is the rotation axis Ib of the wheel B just before closing. This is the tangent of the circle Rc5 with the position Ib5 as the contact. Since the connecting shaft C moves from the position of C5 to the position of C0 from just before the closing to the closing, the “intersection angle Θa of the axis A of the acting body A and the circle Rc5 or the straight line Zc5” becomes an obtuse angle and the wheel B slides. It moves along the moving surface K in the direction of the arrow C in the figure.
When the position of the connecting axis C is provided at a position relatively close to the pivot axis O of the door and the radius of the circle Rc5 is small, the circle Rc5 is greatly separated from the straight line Zc5. As the locus of the rotational axis Ib of the wheel B approaches the circle Rc5, the expansion and contraction of the pulling spring V accompanying the movement of the wheel B decreases, but when the wheel B does not move greatly as shown in FIG. 69, the rotational axis Ib of the wheel B There is no difference even if the locus is close to the straight line Zc5. In this case, the shape of the sliding surface K may be a straight line as shown.

The switchgear of FIGS. 69 (a) to 69 (c) is compared with the device of Patent Document 10. FIG.
Patent Document 10 is a gas damper stage in which the link A in FIG. 69 is piston-moved by the air pressure in the cylinder, and the force for energizing the link A in FIG. 69 varies depending on the air temperature in the cylinder. Thus, the distance that the wheel B moves away from the pivot axis O of the door is adjusted to adjust the rotational moment acting around the center of rotation, thereby stabilizing the operability.
69 (a) to 69 (c) and the device of Patent Document 10 have a sliding surface K in a direction away from the center of rotation, and the rotational moment at the distance between the line of force and the center of rotation. This is the same in that the sliding surface K rotates with the rotation of the door and the movement of the wheel B is started by the rotation of the opening / closing body.
However, Patent Document 10 changes the speed of the subsequent rotation and the magnitude of the working force by moving the wheel in the middle of the rotation, like the opening / closing device of FIGS. 69 (a) to (c), By moving the wheel in the middle of rotation, the previous rotation and the subsequent rotation are not clearly distinguished. Further, Patent Document 10 has no meaning in the previous rotation, and the wheel B is stopped in the vicinity of the pivot O of the door as in the opening / closing device of FIGS. It does not realize constant speed motion without acceleration in the range. Further, it is not a technique for downsizing the apparatus by the ratio between the rotational force and the sealing force.

A mechanism for braking the inertial force will be described with reference to FIGS.
The wheel B stops at a position close to the pivot axis O of the door in the “(A) range” and moves in the “(A) range”. Although the “intersection angle Θa with the moving surface Zk” becomes an obtuse angle, the position at which the movement starts is different depending on the magnitude of “rolling friction between the wheel B and the sliding surface K”. In the embodiment shown in FIG. 69 (c), in order to make the time when the wheel B starts moving on the sliding surface K constant, the wheel BB is attached to the working body A, and the wheel BB contacts the door frame W to act. The body A is rotated so that the wheel B starts to move on the sliding surface K.
The state shown by the solid line in FIG. 69 (c) shows a state when the wheel BB contacts the door frame W, and C10 shows the position of the connecting shaft C at this time. C5 indicates the position of the connecting shaft C when the “intersection angle Θa between the axial line Za of the acting body A and the sliding surface Zk” becomes an obtuse angle. Since the wheel BB is in contact with the door frame W when the position of the connecting shaft C moves from C10 to C5, the push spring U contracts to give resistance to the rotation of the door. FIG. 69C illustrates a case where the gradient of the sliding surface K is larger than the “closed door surface D0” compared to FIG. 69B, but the sliding surface K slides with respect to the “closed door surface D0”. The larger the slope of the surface K, the smaller the compression of the push spring U at this time, and the less resistance to the rotation of the door.

The force of the pulling spring V is weak immediately before closing, and when the wheel BB abuts on the door frame W and the wheel B starts to move on the sliding surface K, the pushing spring U may be contracted. The movement of starting to move is not performed by the force of the pulling spring V but by the inertial force attached to the door. When the door is closed from a position where it is greatly opened, an inertial force is attached to the door, and the door is brought into contact with the door frame W immediately before closing and is not stopped, but is decelerated and sealed.
If the door closes from a slightly open position, inertial force is not attached to the door, but in the process of opening the closed door, the spring functions as "rotating means in the range of (i)" when the door is opened slightly. And it has enough power to seal the door.
The position of C30 shown in FIG. 69 (b) is a position where the door is slightly opened in the process of opening the door, and the “intersection angle Θa between the axis A of the acting body A and the sliding surface Zk” becomes an obtuse angle. The position of the axis C is shown, which is the same as the position “position C30 in the middle of closing from the position where the door is largely opened” shown in FIG. 69 (a). When the door is closed from the position of C30 in the process of closing the door, the wheel B is in the vicinity of the door pivot O, and when the door is closed from the position of C30 in the process of opening the door, the wheel B is separated from the door pivot O. In position.
When the hand is released from the position of C30 in the process of opening the door, the door is closed by the force of the tension spring V. When the door is released after opening the door larger than the position of C30, the wheel B returns to the vicinity of the pivot axis O of the door and then the door is closed by the inertial force attached to the door. Therefore, unless the door is temporarily stopped at the position of C30 in the process of closing the door, the opened door does not stop halfway and does not become sealed.

69 (d) to 69 (f) illustrate a mechanism for braking the inertial force attached to the door. When the inertial force attached to the door is large, the brake is applied so as not to be applied when the door is small. It is a mechanism that distinguishes and processes large differences in inertial force according to the position where the handle is opened and the hand is released from the handle.
FIG. 69 (d) shows a mechanism that brakes the inertial force that is attached just before closing when the hand is released from the handle in a position where the door D is largely opened, and FIG. 69 (e) shows a position where the door D is slightly opened. In FIG. 69 (f), the link A that rotates when the door is opened and stops at the standby position is shown in FIG. 69 (f). It is an operation explanation top view explaining processing when it enters in the outside of the range (g) between GG1 and GG2 before it closes by rotating in the return direction in the middle of closing.

The door D rotates about the pivot axis O of the door, and the door D that is largely opened is denoted by D30 and is shown by a solid line in FIG. 69 (d). The slightly open door D is designated as D15 and is shown by a broken line in FIG. 69 (d) and by a solid line in FIGS. 69 (e) and (f). The closed door is designated as D0 and is shown by broken lines in FIGS. 69 (e) and 69 (f).
The link A rotates about the fixed support shaft Sw provided on the door frame W, and swings between G1 and G2. The rotation axis Ib of the wheel is provided at the tip of the link A, and the wheel B is mounted on the rotation axis Ib of the wheel. One of the toggle springs V is attached to the link A, and the other of the toggle springs V is attached to a support shaft Sv provided on the door frame W. When the toggle spring V is on the side close to G2 with the boundary line Z passing through the fixed support shaft Sw and the support shaft Sv, the link A rotates in the direction of arrow A in the figure and contacts the contact G2. Still at position. The wheel B at this time is designated as B30 and is shown by a solid line in FIG. 69 (d).
When the toggle spring V is on the side close to G1, the link A rotates in the direction opposite to the arrow A in the figure, and the toggle spring V comes into contact with G1 and stops. The hitting G1 does not come into contact with the link A, but the toggle spring V makes contact and stops the link A. The wheel B at this time is designated as B15, and is indicated by a broken line in FIGS. 69 (d) and 69 (f) and indicated by a solid line in FIG. 69 (e).

FIG. 69 (d) is an operation explanatory view when the door D is rotated from the position D15 indicated by the broken line to the position D30 indicated by the solid line. In this state, the door rotates while the contact GG1 contacts the wheel B15, and the link A rotates in the direction of the arrow A in the figure and contacts the contact G2. At this time, the door D30 is located far enough away from the wheel B30.
The state indicated by the broken line in FIG. 69 (d) shows a state in which the door D is in the position D15 in the process of closing the door and the door rotates while the contact GG2 contacts the wheel B30. When the door D rotates in the closing direction from the position of D15, the wheel B presses the door D to rotate in the opening direction by the urging force of the toggle spring V and resists rotation in the closing direction. That is, the door D rotates from the position D30 to the position D15 and brakes the inertial force.

FIG. 69 (e) shows a state in which the door further rotates in the closing direction and the link A rotates in the direction opposite to the arrow A in the figure and the wheel B returns to the position B15. Even if the door rotates further in the closing direction, the wheel B remains at the position B15.
FIG. 69 (e) is an operation explanatory view showing that the wheel B remains at the position B15 when the door D is rotated from the position D0 indicated by the broken line to the position D15 indicated by the solid line, and D15 indicated by the solid line In the process of closing the door from the position, the door D does not contact the wheel B.
When the door rotates in the closing direction from the position of D15 where the door is slightly opened, the inertial force attached is small and the brake is not applied thereto.

When the door is opened and the wheel B is stationary at the position B30, the door GG1 passes without turning right into the wheel B, and the wheel B at the position B30 hits GG1 and GG2. Enter the range outside the range between If the door closes with the wheel B at the position of B30, the wheel B will again fall within the range between GG1 and GG2 and the contact GG2 will abut, but before the door closes When the link A rotates in the direction opposite to the arrow A in the figure and stops at the position of the wheel BB15, the wheel B does not return into the range (範 囲) but stays in the outside range. The state shown by the solid line in FIG. 69 (f) is a state in which the outer side of GG1 comes into contact with the wheel B remaining in the outer range in the process of closing the door, and the wheel B is moved from the position B15 to the position B0. Is shown. A wheel B15 indicated by a broken line indicates a state in which the door further rotates in the closing direction and the wheel B returns to within the range.
Although the toggle spring V is stationary at two stationary positions, it can be rotated in the direction returning from the stationary position, and an accident that does not maintain the standby state as described above may occur. The braking function in FIG. 69 (f) is designed to be able to return even in such a situation.

As shown in FIG. 69 (d), when the brake is applied to the inertial force while the wheel B is in contact with the contact GG2, the intersection angle between the axial center line of the link A and the contact GG2 is initially when the wheel B contacts the contact GG2. Although it is close to a right angle and resists rotation in the closing direction of the door D, when the crossing angle passes a right angle, it immediately stops resisting and the door rotates without braking. That is, this is the same as the state in which the door D rotates without contacting the wheel B as shown in FIG. If the door D is only slightly rotated as shown in FIG. 69 (e) to seal the door, the door shown in FIG. 69 (d) will be sealed even if the door stops rotating. Become.
If the door is heavy, there is no difference between the magnitude of the force that rotates the door and the magnitude of the sealing force, and if a large force is not required when the latch is recessed, the spring force should be the force that rotates the door. It has a sealing force at the end of the door rotation. 69 (d) to 69 (f) are effective in such a case. If the door is sealed by releasing the hand from the position where the door is slightly opened, the door is greatly opened and the hand is released. This is the same even if the hand is released from a slightly opened position, and the door is quietly sealed. If the opening / closing device of FIGS. 69 (d) to 69 (f) is provided with a biasing means that prevents the spring force from acting greatly on the door as the door is opened, the door can be opened without having a "switching means". Can be sealed gently

70 (a) and 70 (b) show an opening / closing device in which the link A in the embodiment of FIG. 6 is replaced with a leaf spring VW. FIGS. 70 (c) and 70 (d) show the link A and the rotating body J in the embodiment of FIG. The crank mechanism is an opening / closing device that replaces the leaf spring VW, and one of the fulcrums at both ends of the leaf spring is attached to the door frame W via the restraining means that can be released to the door D.
70 (a) and 70 (b), a wheel rotation shaft Ib is provided at one end of the leaf spring fulcrum, and the wheel B is mounted. The releasable restraining means is a reciprocating passage of the wheel B provided in the door frame W, and is a slot H. In place of the wheel B, a slot-like groove H of the reciprocating passage and a slider with little friction may be fixed to one end of the leaf spring fulcrum.
FIGS. 70 (a) and 70 (b) are slider link devices similar to FIGS. 6 and 57, and “wheel B with less resistance to movement” is employed for the slider of the present invention.
70 (c) and 70 (d), one end of the leaf spring fulcrum is connected to the connecting shaft P at the tip of a link A that rotates about a fixed support shaft Sw provided on the door frame W. G1 and G2 are provided around the fixed support shaft Sw, and the link A swings between G1 and G2.

70 (a) and 70 (c) show a state where the wheel B does not move at a position close to the door pivot O in the "range from fully open to just before closing (A)". A state of moving on a circumference Ro centering on O in the direction of arrow B in the figure is shown. The leaf spring VW bends in a U-shape, the support reaction force acting on both ends of the spring acts in a direction substantially perpendicular to the axial center direction of the spring, the direction of the force acting on the door is substantially parallel to the door surface, and the diameter of the circular motion of the door Work in the direction. The same applies to the pressing spring of the coil spring instead of the leaf spring, and the pressing spring bends in a U-shape, and the support reaction force acting on both ends of the spring acts in a direction substantially perpendicular to the axial direction of the spring and acts on the door. FIGS. 70 (b) and 70 (d) work in the radial direction of the circular motion of the door and are substantially parallel to the door surface. FIGS. 70 (b) and 70 (d) show that the connecting shaft C is “closed door” in the “range from just before closing to closing”. 70B, the wheel B moves away from the vicinity of the door pivot O and moves away from the door pivot O in FIG. 70D. Indicates the state.
The leaf spring VW approaches a straight line, the supporting reaction force acting on both ends of the spring acts in the substantially axial direction of the leaf spring VW, and the direction of the force acting on the door is substantially perpendicular to the door surface and in the circumferential direction of the circular motion of the door. work.

The door D45 shown in FIGS. 70 (b) and 70 (d) shows the open position of the door which returns to the vicinity of the door pivot O in the process in which the wheel B or the connecting shaft P moved to a position far from the door pivot O opens the door. However, the wheel B or the connecting shaft P is different from the position of the door that instantaneously moves in the vicinity of the door pivot O in the process of closing the door. As in the embodiment of FIG. 57, even if the door is opened a little and the hand is released, it does not stop.
In FIG. 70 (b), since the collision noise is generated when the wheel B moves from one end of the long hole H to the other end, the shock absorbing material Ge is attached to both ends of the long hole H. .

71 is an embodiment in which a leaf spring is attached in place of the rotating body J of FIG. 7. FIG. 71 (a) is in a fully open state, FIG. 71 (b) is a state diagram immediately before closing, and FIG. It is a state figure at the time of closing. FIG. 71 (d) is a state diagram when the closed door is opened and the opening / closing device returns.
One end of the leaf spring UW is fixed to a fixed support shaft Sw provided on the door frame W, and the other end is connected to the connecting shaft P of the link A. As the door closes, the curved state shown in FIG. 71 (a) shifts to a straight line shown in FIG. 71 (c). The rotating body J is rotatably supported around the connecting shaft C, and is biased by the leaf spring UW so as to come into contact with Gc when the connecting shaft P is in the “(A) range”. When the axis P is in the “(range)”, it is urged in a direction away from Gc by the leaf spring UW.

71 (a)-(b), in the process of closing the door, the compression force of the link A is transmitted to Do and the door D rotates in the direction of arrow A in the figure, but the compression force of the link A is parallel to the door surface. Weakly acts on door D. As shown in FIG. 71 (b), the wheel B comes into contact with the door frame W just before closing, and the wheel B receives a force in a direction away from the door surface. When the wheel B comes into contact with the door frame W, there is no variation when the “switching means” is started, and the door is also decelerated.
As shown in FIG. 71 (c), when the wheel B hits and moves away from Gc, the line of action of the compression force of the link A moves, but when the support shaft away from the door pivot O moves, The distance from the pivot axis O of the door does not increase compared to the case where the support shaft at a position close to the pivot axis O moves.
FIG. 71 (d) shows a state in which the closed door is opened and the closing device is restored. As the wheel B moves along the sliding surface K, the wheel B comes into contact with the door surface again.
The opening angle θd1 of the door when the door B is opened and the wheel B comes into contact with the door surface again is larger than the opening angle θd2 of the door when the wheel B is separated from the door surface when the door is closed.

The embodiment of FIGS. 72 and 73 employs the spring mechanism described in FIGS. 3 to 5 for driving the link device. When the door is closed, the range from “a range where a weak force acts on the door” is applied. When the door is opened, the door rotation angle of the door Θd is changed from “range of strong force acting on the door” when opening the door to “weak range of force acting on the door ( Even if the door rotation angle is greater than the door rotation angle door Θd and the rotation is decelerated to near the stop during the closing of the door, the hand should be opened slightly. Does not stop even if you release the button.
In FIG. 72, a connecting shaft C provided on the door and a fixed support shaft Sw provided on the door frame W are connected by a tension spring V via a link A, and the rotating body Jc is a rotating support shaft Ij provided on the door D. Rotate around the axis.
The connecting shaft C is provided at the tip of the rotating body Jc, and the link A rotates about the connecting shaft C. One end of the tension spring V is attached to the support shaft Ibb at the tip of the link A, and the other end is attached to the fixed support shaft Sw provided on the door frame W.

FIG. 72 (a) shows a state of rotation in “range from fully open to just before closing (A)”, and FIG. 72 (c) shows rotation in “range from just before closing to the time of closing (Yes)”. Indicates the state to perform. As shown in FIG. 72 (a), when the connecting shaft C is on the fully open side of the door with the axial center Zv of the tension spring V as a boundary, the link A is opposite to the direction indicated by the arrow a in FIG. It is urged to rotate and the contact G attached to the link A comes into contact with the rotating body Jc. As shown by a solid line in FIG. 72 (b), in the process of closing the door, the link A is switched from the (A) rotating means to the (I) rotating means.
When the connecting shaft C crosses the axis Zv-10 of the tension spring V and moves from the fully open side to the fully closed side of the door with the axis Zv of the tension spring V as a boundary, the link A is shown with the connection axis C as the axis. Rotating in the direction of arrow A, the hit G moves away from the rotating body Jc, and the wheel B moves along the sliding surface K provided on the door frame W as shown by the broken line in FIG. . That is, the (a) rotating means and (ii) rotating means differ in the position of the support shaft Ibb at the other end of the tension spring V, and have different structures. The “distance Lv between the line of action F of the force acting on the door and the center of rotation” changes from Lv60 shown in FIG. 72 (a) to Lv5 shown in FIG. 72 (c).

In the state shown by the broken line in FIG. 72 (b), the connection axis C is on the fully closed side of the door with the axis Zv of the pulling spring V as a boundary, and the link A is in the direction of the arrow a in FIG. Since the link A is biased to rotate, when the door is opened, the link A rotates in the direction opposite to the arrow A in the figure, and the contact G does not contact the rotating body Jc. It does not return to the structure of the rotating means in contact.
In order for the link A to rotate in the direction opposite to the arrow A in the figure from the state of the rotating means in which the contact G does not abut against the rotating body Jc, the connecting shaft C is Zv− shown in FIG. 30 must be moved from the fully closed side to the fully open side. The opening angle Θd of the door when returning to the structure of the rotating means abutting from the structure of the rotating means when the door is opened (a) and the structure of the rotating means when the door is closed (a) This is different from the door opening angle Θd when moving to the structure of the rotating means.

That is, when the door is opened, until the connecting shaft C exceeds the axis Zv-30 of the spring V, the door is felt heavy because a strong sealing force is applied to the door, but the connecting shaft C is the axis of the spring V. Beyond Zv-30, the door feels light because a weak rotational force is acting on the door.
When the connecting shaft C is on the fully open side of the door with the shaft core Zv-30 of the spring V as the boundary and the hand is released from the handle, it is switched from (a) rotating means to (ii) rotating means and closed. However, when the hand is released from the handle on the fully closed side of the door with the axial center Zv-30 of the spring V as a boundary, it is closed by the rotating means (ii).
When the values of Lv60 shown in FIG. 72 (a) and Lv5 shown in FIG. 72 (c) are positive, the value of Lv10 shown in FIG. 72 (b) is negative, and the pulling spring V is attached in the direction to open the door. Rush. At this time, the wheel BB moves along the door frame W.
Even if the door stops just before the door closes, not only does the link device continue to rotate, but when you open the door, the door stops even if you release your hand at the `` position where the door stops just before the door closes ''. It will never remain.

If the latch is in contact with the door frame W when the wheel B30 contacts the sliding surface K as shown by a broken line in FIG. 72 (b), the value of Lv30 shown in FIG. The magnitude of the force acting on the door when the latch abuts against the door frame W is smaller than the force acting at the time of sealing so as to be smaller than the value of Lv5 shown in c).
The connecting shaft C is provided at the tip of the rotating body Jc, and even if the magnitude of the force acting on the door when the latch abuts against the door frame W does not cause the latch to be recessed, the rotating body Jc and the door D When the push spring U is inserted between the two and the push spring U contracts, the rotating body Jc rotates in the direction of the arrow D in the figure around the rotation support shaft Ij, and the wheel B moves in the direction of the arrow C in the figure. To do. The “intersection angle Θb between the line of action Fb of the wheel B pressing the sliding surface K and the sliding surface K” is the value of Θb30 shown in FIG. 72 (b) is the value of Θb5 shown in FIG. 72 (c). The smaller the wheel B, the easier it is to move.

As the wheel B moves, the “force Fb that the wheel presses the sliding surface” increases, and acts on the door via the push spring U to seal the door.
As shown in FIGS. 57 (d) (e), 58 (d), 62, 63 (b) and (c), the pressing spring U shown in FIG. The other attachment portion is attached to the connection shaft C to the fixed support shaft Sw of the door frame W, and is a means for making the attachment portion movable and expanding and contracting.
FIG. 51 shows one attachment portion Cj of the opening / closing device connected to the connection shaft C of the door so as to be extendable and contractable, and FIG. 52 is attached rotatably.

50 and 51, the pressing spring U and the torsion spring UV are components for detecting the inertial force attached to the door, and are means for transmitting the inertial force input from the door to the opening / closing device. It is also a means for transmitting rotational force. The means for preventing the continuous sealing does not function except when a special load such as a strong wind is applied. However, in the normal use range, the switchgear is not affected by the inertial force. The rotating body J of the embodiment rotates more in the sealed state than in the case where the push spring U and the torsion spring UV are not inserted, so that the rotational force transmitted from the opening / closing device is relieved and the time required for sealing is increased. To do.
In the present invention, the opening / closing device operates greatly with respect to “a slight rotation of the door until the latch comes into contact with the door frame W and the door comes into close contact with the door stop”, and the attachment portion has inserted the expansion joint. By doing so, the operation is further increased.

72. The expansion joint inserted in FIG. 72 is a rotating body Jc and a pressing spring U inserted between the connecting shaft C and the door D, and the rotation of the link A and the rotating body Jc is larger than when these are not inserted. Become.
When the sealing force acts weakly, the rigidity of the push spring U is set to be extremely small. When the stiffness of the push spring U is zero and the push spring U is removed from the expansion joint, the switching means functions just before closing, and when the link A starts to rotate, no rotational force is transmitted from the switchgear. Thus, the door continues to rotate and close with inertia force without depending on the spring force of the opening / closing device, and the space between the connecting shaft C and the door D is expanded. The link A begins to move along the sliding surface K, and the rotational force is transmitted again from the opening / closing device, so that the space between the connecting shaft C and the door D is narrowed. When the rotational force from the switchgear is once insulated and transmitted again in this way, the door that is decelerated and tries to be stationary can be moved, and the static inertia is attached to the door that has been moved only by the dynamic inertia. The door where the inertia works is moved again. Thus, a long time elapses until the latch comes into contact with the door frame W and the door comes into close contact with the door stop.

Even when the magnitude of the force acting on the door when the latch contacts the door frame W is not large enough to seal the door, the wheel moves the sliding surface as the wheel B moves on the sliding surface K. The pressing force Fb approaches a state where it overlaps with the axial center line Za of the link A, and the magnitude of the force acting on the door grows to a size that seals the door.
When the latch abuts against the door frame W, the amount of force acting on the door is less than the size that seals the door. It takes a long time for the contact door to come into close contact with the door stop.
Further, the closer the position of the fixed support shaft Sw is to the rotation axis C5 of the link A, the less the expansion and contraction of the tension spring V and the slower the rotation of the link A.

In FIG. 73, the connecting shaft C provided on the door D and the fixed support shaft Sw provided on the door frame W are connected via the link A by the “string Sc in which the tension springs Vc are connected in series”. May be a string or a coil spring that provides a tensile force by expanding and contracting like a rubber string, as long as it moves along the pulley Bc and provides a tensile force. The pulley Bc is mounted on the tip of the rotating body Ac, and the rotating body Ac rotates about a rotation support shaft Qc provided on the door frame W. The link A rotates about the connecting shaft C.
One end of the “string Sc in which the tension springs Vc are connected in series” is attached to the support shaft Sa at the front end of the link A, and the other end is attached to the fixed support shaft Sw provided on the door frame W. 73, the support shaft Sa at the front end of the link A to which one end of the string Sc is attached is located farther from the connecting shaft C from the door pivot O, and the direction in which the link A faces is different from the case of FIGS. Is different.
FIG. 73 (a) shows a state of rotating in a fully open state, FIG. 73 (b) shows a state of rotating in a “range from fully open to immediately before closing (A)”, and FIG. 73 (c) shows “from immediately before closing to closing. It shows the state of rotating in the range up to (i). FIG. 73 (d) shows a state where the door is fully closed, and FIG. 73 (e) shows a state where the closed door is slightly opened.

Assuming that the pulley Bc is in the middle and the support shaft Sa side of the cord Sc is the Sca fixed support shaft Sw side, as shown in FIG. 552 (a) (b), the connecting shaft C is connected to the door with the strap Sca as the boundary. When the link A is at the fully open side, the link A is urged to rotate about the connection axis C in the direction opposite to the direction of arrow A in the figure, and the contact Ga attached to the link A contacts the door D.
As shown in FIGS. 73 (c) and 73 (d), when the connecting shaft C crosses the axis of the string Sca and moves from the fully open side of the door to the fully closed side with the axis Zv of the string Sca as a boundary, the link A is Rotates in the direction of arrow A in the figure with the connecting shaft C as the axis, hitting Ga leaves the door D, and the sliding surface K provided on the link A moves along the wheel B as shown in FIG. To come. A sealing mechanism in which the sliding surface K moves along the wheel B will be described later with reference to FIG.

FIG. 73 (b) shows a state in the middle of the range (A) from the time of full opening until just before closing. Since the same tensile force acts on the cords Sca and Scw, the axial center line Zac of the rotating body Ac on which the pulley is mounted at the tip is on the bisector of the angle Θc bent around the pulley Bc of the cord Sc.
The expansion and contraction of the spring Vc is half that when the door is directly pulled when the string Sc is pulled via the movable pulley Bc, so the rotation of the pulley Bc is half of the rotation of the door. Since the rotation of the axial center line Zac of the rotating body Ac around the rotation axis Qc is small and the expansion and contraction of the tension spring Vc is small, the energy of the spring given to the door D is small and the acceleration of the door D is also small.
In the “range from fully open to just before closing (A)”, the rotating body Ac rotates around the rotation axis Qc, the pulley Bc rotates toward the door frame W, the length of the tension spring V decreases, and the door D It rotates in the direction of arrow B in the figure. The length of the spring Vc decreases as the connecting shaft C approaches the fixed support shaft Sw.

The length of the spring Vc decreases as the pulley Bc moves in the direction of arrow B in the figure between the connecting shaft C and the fixed support shaft Sw, and the length of the spring Vc decreases as it moves in the direction opposite to the arrow B in the figure. To increase. A pulley Bc50 indicated by a broken line in FIG. 73 (b) is a case where the rotation of the door is delayed, the strength of the spring is increased, and the action line F of the force acting on the string Sca is moved away from the door pivot O to accelerate the door. . In the pulley Bc70 shown by the broken line in FIG. 73 (b), the rotation of the door proceeds, the strength of the spring is weakened, and the action line F of the force acting on the string Sca approaches the door pivot O to decelerate the door. .
As shown in FIG. 73 (c), the door rotates while the contact Gac provided on the rotating body Ac contacts the door frame W or the pulley Bc contacts the door frame W and the movement of the rotating body Ac stops. If it continues, the length of the tension spring V will be extended and the rotation of a door will be decelerated.

As shown in FIG. 73 (c), the link A rotates from the state parallel to the closed door surface D0 in which the line of action Fb of the sliding surface K pressing the wheel B is closed, as shown in FIG. 73 (d). As shown in the figure, the state gradually shifts to a right-angled state, but at the same time, the link A rotates greatly so that “the sliding surface K presses the wheel B to seal the door” works. Here, by bringing the center of rotation C of the link A closer to the “position where the string Sc bends about the pulley Bc”, the expansion and contraction of the spring is reduced even if the link A rotates greatly, and the spring is finally applied at the end of the rotation of the link A. The power of will not weaken.
If it becomes a right angle state at the time of sealing, the closed door cannot be opened. Therefore, the door is sealed at a position where it does not gradually reach a right angle state from a state parallel to the door surface.

When opening the closed door, the strings Sca and Scw are not in the closed state as shown in FIG. 73 (c), but are in the open state as shown in FIG. 73 (e), and the closed state when the door is closed. The rotation angle Θds of the door when opening from the door is different from the rotation angle Θdo of the door when closing from the open state when opening the door. As a result, just before the door is closed, the spring force is applied weakly, or even if the door is stopped by applying resistance, the door remains stationary even when the door is opened wide and closed and closed small. Never become.

74 (a1) and (a2) relate to the string Sc used in FIG. 73, and FIG. 74 (a1) shows that the string Sc moving along the pulley Bc is flattened and the cross-sectional shape changes, along the pulley Bc. The displacement δ is generated between the axis line of the string Sc that moves and the axis line of the string Sc that is away from the pulley Bc, so that the moving speed of the string Sc along the pulley Bc is reduced. If the material of the string is elastic like rubber, the pulley will wrap around the string while wrapping, so the moving speed of the string along the pulley Bc will be slow, and if the string is a hard material like silk thread, There is little frictional resistance between dried fish, and the moving speed of the string along the pulley Bc is increased.
FIG. 74 (a2) shows a case where a chain is used for the string Sc. As in FIG. 74 (a1), the axis of the string Sc moving along the pulley Bc and the axis of the string Sc separated from the pulley Bc are shown. Deviation δ occurs between the core wire. The magnitude of the deviation δ pulsates, and the magnitude of the spring force also pulsates. The same effect can be obtained when a string is used instead of a circle by using a string without using a chain, and making the pulley a polygon instead of a circle.
By decelerating the moving speed of the string Sc along the pulley Bc, the door closing speed is reduced in the “range from fully open to just before closing (A)”, and the “range from just before closing to the closing time ( ")", The rotational speed of the link A around the connection axis C is reduced, and a long time is required for sealing.

When the closure device is driven by a single spring, the maximum value of the spring force required to rotate and seal the door is the spring force that is weakest at the end of the door rotation. The spring force is set to a minimum by adjusting the weakest spring force to the minimum at the end of rotation. In this way, the force when opening the door is minimal, and the impact sound when closing is minimized.
74 (b1) to (b3) and (c1) to (c3) are mechanisms for sealing the door with the weakest spring force at the end of the rotation, and the wheel B and the sliding mechanism. The moving surface K is the wheel B and the sliding surface K shown in FIG. 73, and the wheel B is attached to the tip of the link Ab that rotates about the rotation axis Ib provided on the door frame W. Rather than being fixed to W, it is revolved around the rotation Ib. As in FIG. 52, the rotational force of the closing device is transmitted to the door via the rotating expansion joint, and the sealing takes a long time.

The force Fb at which the wheel B presses the sliding surface K becomes stronger as a sealing force as it approaches the straight line Zibc passing through the rotating shaft Ib and the connecting shaft C. Yes. In FIGS. 74 (b1) to 74 (b3), the wheel B enters while eliminating the sliding surface K in the approach track, and in FIGS. 74 (c1) to 74 (c3), the wheel B slides outside the approach track. Enter while including the moving surface K.
When the latch contacts the door frame W, as shown in FIGS. 74 (b1) and 74 (c1), the sliding surface K collides with the wheel B or the door frame W and receives resistance, but continues to rotate. When the latch abuts against the door frame W, the sliding surface K gradually moves along the wheel B even though the rotational force M around the connecting shaft C has no force to seal the door. As the wheel B is attracted, the latch is barely recessed and the door is rotated.

No matter how small the rotational force acting on the door, the door's dynamic inertial force will accelerate as long as the force continues to be applied. The force required for sealing is determined by the door, but if dynamic inertia force participates in sealing, the dynamic inertia force varies depending on the opening angle of the door when the door is opened and released. Is not constant. It is desirable to remove the dynamic inertia force at the time of sealing so that a constant force works to make the impact sound at the time of sealing constant.
It has already been explained that if the door opening angle is different when switching to a strong force when the door closes and when the door is switching to a weak force when opening, the door will not remain stopped even if the door is stopped during closing. ing.

The sealing mechanism described in FIGS. 75, 76 and 77 applies a brake just before closing, as in the sealing mechanism of FIG. 66, and resists the biasing of the spring in the middle of closing. It does not increase the force of the spring so as to overcome the resistance by resisting the spring force in the entire range of rotation of the door as shown in FIG. It only removes the inertial force and does not increase the spring force more than necessary.
In any one of the connecting shafts of the links constituting the link device, the speed reducing means is connected when the crossing angle of the two links connected to the connecting shaft becomes a minimum value or a maximum value immediately before closing. The operation of the link device is temporarily stopped by restricting the rotation of the two links around the shaft, and the restriction is released at the time of sealing.
An adjustment bolt is provided on one link connected to the connecting shaft, and a contact abutting against the adjustment bolt is provided on the other link. When the angle of intersection between one link connected to the shaft and the other link is minimized, the adjustment bolt and the contact are in contact with each other, and the door is temporarily stopped almost immediately before the door is closed. It is to make. When the door is pressed against the door, the adjustment bolt and the contact are separated.

In FIG. 75, as shown in FIGS. 56 (c) and 63, the rotating body J is pivotally supported on the fixed supporting shaft Sw, the link A is connected to the connecting shaft P provided at the tip of the rotating body J, and the link A is connected to the door. This is a structure that is connected to a connecting shaft C provided in D, and the shaft cores of the two links approach a straight line when sealed, and a large axial force acts on the link A.
In FIG. 75 (a), the fully opened state of the door is indicated by a dotted line, and in FIG. 75 (b), the closed state of the door is indicated by a solid line. When the rotating body J rotates about the fixed support shaft Sw in the direction of the arrow A in the figure, the door D rotates about the pivot axis O of the door in the direction of the arrow B in the figure, and the rotation directions of the rotating body and the door are opposite to each other. It becomes. 75 (c) shows the operation of the link device of the connecting portion before and after full opening shown in FIG. 75 (a), and FIG. 75 (d) shows the operation before and after closing shown in FIG. 75 (b). 75A and 75B, the links Ji, Ai, Di (i = 0, 1, 2,...) And the connection axes Pi, Ci (i = 0, 1, 2,...) Indicated by dotted lines. -) Indicates the movement of the position of each link and each connecting axis that changes from moment to moment.

In the operation of the link device of the connecting portion before and after full opening shown in FIG. 75 (c), when all of the door pivot axis O and the connecting shafts C6 and P6 are on a straight line T6, the rotating body J rotates in the direction indicated by arrow C in the figure. The rotation angle is the maximum, and the rotating body J is loaded with the spring force to rotate in the direction of arrow A in the figure, so the position of the connecting shaft C is in the position moved in the two directions with the straight line T6 as a boundary. When the connecting shaft C moves in the bi-direction, the connecting shaft C moves in the bi-direction when the connecting shaft C is in the position moved in the bi-direction. When the position of the connecting shaft C moves away from the straight line T6, the door hits G7 and comes to rest in the fully open state. When the position of the connecting shaft C moves away from the straight line T6 to the lower side, the door hits and hits G0. It starts to rotate.

FIG. 75 (d) illustrates the closing operation of the link device at the connecting portion before and after the door is closed. In the process of rotating the rotating body J from the position of J3 toward the position of J0, the rotating body J is at the position of J1 and the connecting shaft P is at the position of P1, and is connected to the fixed support shaft Sw and the pivot axis O of the door. When all of the shaft connecting shafts P are on the straight line T1, the distance between the connecting shaft P and the door pivot O is minimized, so that the angle Θ at which the link A and the door D intersect is minimized.
When the rotating body J rotates in the direction of arrow A, and the position of the connection axis P is closer to the P2 side than P1 toward the position P1, the crossing angle Θ between the link A and the door D decreases, and the position of the connection axis P The crossing angle Θ between the link A and the door D increases when it is closer to P0 than P1 and toward the position P0.

The adjusting bolt Ga shown in FIG. 75 (b) passes through a through hole provided in the leaf spring Pa attached to the intermediate part of the link A, and a screw is loaded into the through hole, and the position of the tip of the adjusting bolt Ga Enters and exits from the leaf spring Pa and is fixed.
When the position of the connecting shaft P is on the P2 side with respect to P1, if the tip of the adjustment bolt Ga hits the “contact Gb provided on the door”, the position where the tip of the adjustment bolt Ga hits the contact Gb Since the crossing angle Θ between the link A and the door D decreases when going from the position P1 to the position P1, the tip of the adjustment bolt Ga pushes and bends the leaf spring Pa, and “the link A around the connection axis C and Resistance is applied to “rotation with door D”.
When the position of the connecting shaft P passes through the position of P1 and goes to P0, the crossing angle Θ between the link A and the door D increases, so that the force that the tip of the adjustment bolt Ga pushes and bends the leaf spring Pa is weakened. The tip of the adjustment bolt Ga is separated from the leaf spring Pa, and the door D hits the door stop G0. When the door is sealed, resistance by the adjusting bolt Ga and the leaf spring Pa is not applied.

"The distance from the position where the tip of the adjusting bolt Ga hits Gb to the position P1" and "the distance from the position where the tip of the adjusting bolt Ga hits away from Gb to the position P1 is equal," The shorter the “distance from the position where the tip of the bolt hits Gb to the position of P1” is shortened, the “range where the tip of the adjusting bolt Ga hits Gb” becomes narrower, and the tip of the adjusting bolt Ga pushes the leaf spring Pa. The amount of pushing and bending is small, and the pushing and bending force is weakened. As a result, the effect of slowing down just before closing the door is reduced.

76 and the structure in which the rotation of the drive unit J is transmitted to the door D by a connecting portion including two links A and AA, and the guide roller B is added to the link device described in FIG. As shown in FIG. 75, by setting the connecting portion of the link device to a state in which it is not temporarily deformed, the door with inertial force is temporarily brought into a state close to being stopped immediately before closing.
The rotating body J is supported by a fixed support shaft Sw provided on the door frame W and rotates in the direction of arrow A in the figure, and the door D rotates about the pivot axis O of the door in the direction of arrow R to close the door. The connecting shaft P provided at the tip of the rotating body J and the connecting shaft C provided at the door are connected by two links A and AA, and the link A and the link AA are connected by a connecting shaft PP.

The guide roller B is mounted on a rotation support shaft Ib provided on the door frame W, and the link A moves along the outer peripheral edge of the guide roller B, and is in contact with the door when it is closed even though it is separated when the door is fully opened.
The link device described in FIG. 13 is “range from fully open to just before closing (A)”, and the direction in which the link AA pulls the door works at right angles to the door surface. In FIG. By moving along the guide roller B, the link AA pulls the door in the direction toward the pivot axis O of the door, and a part of the force transmitted to the door is supported by the guide roller B. Is slowed down.
Also, in the “range from just before closing to the closing time (i)”, the direction in which the link AA pulls the door gradually changes from the direction toward the door pivot O to the right angle, and the sealing force acting on the door gradually increases. To reach a size that can seal the door at the very end. “The door closing speed is also reduced until the latch abuts against the door frame W, the latch is recessed, and the door comes into close contact with the door stop, and the door is quietly sealed.

Link Ji, Ai, AAi, Di, (i = 0, 1) from time to time (i = 0, 1, 2,... 7) from closing (i = 0) to full opening (i = 7). , 2... 7) and the positions of the connecting axes Pi, PPi, Ci (i = 0, 1, 2,... 7), the numerical value in parentheses attached to Ci is connected to the connecting axis Pi. It represents the change in distance from the axis Ci.
The distance between the connection axis Pi and the connection axis Ci is minimum at time i = 4 in FIG. 40912 (a) and at time i = 2 in FIG. 76 (b). Therefore, at this time, the crossing angle Θ between the links A and AA on the connection axis PP is minimized.
FIG. 76 (a) shows a case where the length of the link AA is shorter than that in FIG. 76 (b). Is shown.

The crossing angle Θ between the link A and the link AA changes every moment, decreases as the door closes from the time of full opening, reaches a minimum value immediately before closing, and starts increasing when the door closes.
In FIG. 76, the contact Ga and Gb shown in FIGS. 77 (a) and 77 (b) are attached to the connecting portion PP of the two links, and the angle at which one of the links connected to the connecting shaft and the other link intersect is minimized. In this range, the reduction device is configured so that the contact Ga and Gb come into contact with each other and are separated when the door is pressed against the door.
When Ga and Gb come into contact with each other, the angular deformation of the links A and AA around the connecting portion PP is constrained, and the link device cannot be deformed. After decelerating the closing speed, the angle between the links A and AA is closed and reopened immediately before the door is closed, so that when Ga and Gb are separated again at the time of closing, both do not participate in the sealing force. .
Further, when the contact Ga and Gb come into contact with each other, the connecting shaft C approaches the rotating shaft Ib of the wheel while revolving around the rotating shaft Ib of the wheel. "Force" and "force perpendicular to the door surface" work at the same time, and the door closes while pushing it into the pivot axis O of the door. It is decelerated. Finally, when the door is sealed, the force for pushing the door into the door pivot O is eliminated, and all the forces become the force for sealing the door.

FIG. 77 (a) shows a state where the contact Ga and Gb are in contact with each other, and the leaf spring Gb is bent by the adjusting bolt Ga. FIG. 77 (b) shows a state in which both are separated.
77 (a) and 77 (b), the plate Pa is fixed to the link AA, and a through hole Ha is provided in the plate Pa. Since the adjustment bolt Ga passes through the through hole Ha and is threaded inside the through hole Ha, the adjustment bolt Ga can be taken in and out of the plate Pa by turning the adjustment bolt Ga.
The end of the slide shaft Pb2 having a rectangular cross section is fixed to the link A via the plate Pb1, and a leaf spring Gb is attached to the slide shaft Pb2. The set collar Pb3 is provided with a rectangular through hole Hb, and a slide shaft Pb2 and a leaf spring Gb are accommodated in the through hole Hb.
The set collar Pb3 is movable in the length direction of the leaf spring Gb, the position is determined by a set screw Pb4, and the distance Lb from the contact point between the leaf spring Gb and the adjusting bolt Ga to the set collar can be adjusted.
The end of the leaf spring Gb is a free end, and as the distance Lb increases, the spring stiffness decreases and deforms as a cantilever.
By adjusting the distance La, the magnitude of the resistance applied to the rotational force transmitted from the drive unit J to the door can be adjusted. When the distance La is lengthened, the contact area between the two becomes large, the deceleration effect is large, and the door rotation stops. Further, when the distance Lb is shortened, a strong drag is exerted and the rotational force is greatly resisted.

In FIG. 78 (a), R20 is the distance between the rotation axis Q and the position farthest from the rotation axis Q20 of the wheel BB centered on the position of the rotation axis Q20 of the rotating body J3 when the door is opened approximately 20 degrees. The sliding surface K4 of the rotating body J4 that rotates about the rotation axis I4 coincides with this.
The action line F4 of the force with which the wheel BB presses the sliding surface K4 is a perpendicular line that stands on the sliding surface K4 through the contact point of the wheel BB with the sliding surface K4.
As shown in FIG. 78A, the force action line F4 passes through the rotation axis Q of the rotating body J3 at the moment when the wheel BB contacts the sliding surface K4, so that the rotating body J3 does not rotate. Therefore, before the wheel BB contacts the sliding surface K4, the wheel BBB is pressed by the rotation of the cam body J2 and the door rotates, but the rotating body J3 cannot rotate in the direction of arrow → e in the figure around the rotation axis Q20. Then, the door D cannot rotate.

The rotating body J4 can rotate around the rotation axis I4 and is pressed against G4 by a pressing spring U4. Therefore, as shown in FIG. The door D can continue to rotate for a while while rotating the rotating body J4 in the direction of the arrow → G in the figure. When the rotator J4 rotates in the direction of arrow → G in the figure, the wheel BB moves on the sliding surface K4 having a gradient with respect to the traveling direction.
After the door D rotates for a while, the rotating body J3 comes into contact with the cam body. The action line F3 of the force with which the cam body J2 presses the wheel B when the rotating body J3 contacts the cam body is closer to the rotating shaft O side of the door D than the rotating shaft Q of the rotating body J3. Even if the upward slope of the surface K4 is climbed, the rotating body J3 is rotated in the direction of arrow → e in the figure.

When the rotating body J3 rotates in the direction of arrow → e in the figure, the line of action of the force by which the sliding surface K4 of the rotating body J4 presses the wheel BB passes through the opposite side of the rotating shaft Q from the rotating shaft O. The rotating body J3 can be rotated by the rotation of the door D. When the position of the rotary shaft I2 is close to the closed door D0, the cam body J2 and the wheel BBB come into contact again even if the wheel B is separated from the cam body J2. The rotating body J3 is rotated in the direction of arrow → e in the figure by the rotating shaft. The wheel BB moves on the sliding surface K4 in the direction of the arrow → H in the figure, and is included in the recess N4 at the end of the sliding surface K4 to seal the door as shown in FIG. 78 (c). Since the rotation axis I2 is attached not to the door but to the door frame in the same manner as the recess N4 at the end of the sliding surface K4, the door can be sealed.

In FIGS. 78 (a) and 78 (b), the rotating body J4 rotates by the inertial force of the door, but it is not the push spring U4 but the slope of the sliding surface K4 that resists the rotation of the rotating body J3. Therefore, the force of the pressing spring U4 does not need to be strong, and it is sufficient if the rotating body J4 has a force to return to the original unloaded state when the wheel BB reaches the end of the sliding surface as shown in FIG. 78 (c). . When the sliding surface K4 does not rotate, the rotation of the rotating body J3 may cause the door D to rotate, but when the sliding surface K4 rotates, the rotating body J3 may rotate while rotating in the closing direction. If the wheel B is at the end of the sliding surface and the rotating body J4 is rotated in the direction of arrow → H in the figure to return to the original state, the door does not rotate in the opening direction and the push spring U4 does not rotate. Will be restored.
When the sealed door shown in FIG. 78 (c) is opened, since the wheel BBB is in contact with the cam body J2 for a while after opening, the cam body J2 is rotated by the wheel BBB. The body J3 does not participate in the rotation of the cam body J2.

The cam body sliding surfaces shown in FIGS. 34 to 36 keep the moment acting around the rotating shaft Qj of the cam wheel rotating body constant, assuming that the pressing force Fb acting on the cam wheel B is constant. However, as the door that works with the spring is opened, the force of the spring changes, and since the fulcrum of the spring moves in the space, the direction of the force changes, and the pressing force Fb acting on the cam wheel B is not always constant.
The cam body sliding surface shown in FIG. 79 keeps the moment around the cam wheel rotating body rotation axis Qj constant when the pressing force Fb acting on the cam wheel B changes.
FIG. 79a) shows a case where the pressing force Fb becomes weaker as it opens, and the “distance between the action lines Fb0, Fb1, Fb2,. Thus, the rotational moment around the cam wheel rotating body rotation axis Qj is kept constant.
FIG. 79B shows a case where the pressing force Fb becomes stronger as it opens, and the rotational moment around the rotation axis O is kept constant by gradually decreasing the distance.

The drawing method of “the vortex K of the sliding surface of the cam body that exerts a constant rotational moment around the rotational axis Qj of the cam wheel rotating body” when the force Fb that presses the wheel changes will be described.
.. And cam wheels according to the pressing force acting lines Fb0, Fb1, Fb2,... According to the magnitude of the pressing force acting on the wheel B at each point b0, b1, b2,. Distances Lb0, Lb1, Lb2,... With the rotating body rotation axis Qj are determined. The virtual circles Ra0, Ra1, Ra2,... Are centered on the cam wheel rotating body rotation axis Qj, the distances Lb0, Lb1, Lb2,. It contacts the action lines Fb0, Fb1, Fb2,. Arcs R0, R1, R2,... R0, R1, R2,... Are arcs centered on the contacts a0, a1, a2,... With radii a0b0, a1b1, a2b2,. A vortex K of the sliding surface of the cam body is formed by rotating the cam body rotation axis Qk and continuing the rotation.

In FIG. 79, the vortex line KA is a vortex line when the pressing force Fb shown in FIGS. 34 to 36 works constant, and the vortex line Kb shown in FIG. 79A is a vortex when the pressing force Fb decreases as the pressing force Fb opens. In the line, the rate of change in the curvature increases as it approaches the rotation axis Qk as compared to the vortex line KA. The vortex Kc shown in FIG. 79 (b) is a vortex in the case of increasing as the pressing force Fb is opened, and the rate of change in the curvature becomes smaller as the rotation axis Q is approached compared to the vortex KA.
The distances Qkq0, Qkq1, Qkq2,... Between the action lines Fb0, Fb1, Fb2,... Of the respective pressing forces at the position where the cam wheel B has moved and the cam body rotation shaft Qk change, and the pressing forces Fb0, Fb1. , Fb2,... And the distance Qkq0, Qkq1, Qkq2... Between the cam body rotation axis Qk is a moment acting around the cam body rotation axis Qk. In FIG. 34, the moment acting around the cam body rotation axis Qk is the product of the action line Fv of the spring force and the distance rk between the rotation axis Qk.

In FIG. 34, when the tension spring V is along the guide rail Ks around the cam body rotation axis Qk, a change in moment acting around the cam body rotation axis Qk can be measured, and a change in the pressing force Fb can also be measured. The vortex line when the pressing force Fb changes can be drawn by the drawing method described in FIG. Conversely, it is possible to design a pressing force to be applied to the vortex line drawn.
In FIG. 34, from the balance of moments acting around the cam body rotation axis Qk, the product of the “distance Qkq between the pressing force action line Fb and the cam body rotation axis Qk” and the pressing force Fb is “the action of the spring force. It is equal to the product of the distance rk between the line Fv and the cam body rotation axis Qk and the spring force Fv.
Since the product of the “distance lb between the pressing force action line Fb and the rotating body rotation axis Qj” and the pressing force Fb is constant, the change of the pressing force Fb is obtained, and “the pressing force action line Fb and the cam body By measuring the change in the “distance Qkq from the rotation axis Qk”, the change in the product of the “distance rk between the spring force action line Fv and the cam body rotation axis Qk” and the spring force Fv can be calculated. I can do it. According to this calculation, the change in the shape of the guide rail Ks and the spring force in FIG. 34 can be designed.

In FIGS. 35 and 36 and FIG. 37, no matter where the cam wheel B is on the sliding surface K, when the sliding surface K applies a constant pressing force to the cam wheel B, A constant rotational force is provided around the cam wheel rotating body rotation axis Qj. However, with respect to the rotational force around the cam body rotation axis Qk, no matter where the cam wheel B is on the sliding surface K, the cam wheel B exerts a constant pressing force on the sliding surface K and the cam body rotation axis Qk. The constant rotational force around is balanced, and the smells in FIGS. 35 and 36 are not balanced.
In FIG. 37, when the sliding surface K applies a constant pressing force to the cam wheel B, a constant rotational force is provided both around the wheel rotating body rotation axis Qj and around the cam body rotating axis Qk.
The shape of the sliding surface K in FIGS. 35 and 36 is determined by the circular motion of the cam wheel B around the rotating shaft Qj of the cam wheel rotor, but the shape of the sliding surface K is not related to the movement of the cam wheel B.
The shape of the sliding surface K drawn in FIG. 37 (b) is an involute vortex K, not about the cam wheel rotating body rotation axis Qj but around the cam body rotating axis Qk at the center of its own rotation. A constant pressing force acting between the sliding surface K and the cam wheel B is balanced with a constant rotational force, and is a virtual circle centered on its own rotation axis regardless of the position of the wheel B. Determined by size.

The involute vortex line drawn in FIG. 37 (b) causes a constant rotational force to act around the center Qk of the rotating shaft if a constant pressing force of the cam wheel B is applied. In other words, if a constant rotational force is applied around the center Qk of the rotary shaft, the wheel B is moved while applying a constant pressing force.
The moving trajectory of the cam wheel B moving on the involute vortex K is arbitrary regardless of whether the cam wheel B applies a constant pressing force or the wheel B applies a constant pressing force.
In the case of FIG. 37, the cam wheel B revolves around the cam wheel rotating body rotation axis Qj, and when the length of the cam wheel rotating body Jq is infinite in FIG. The movement trajectory becomes a straight line. As shown in FIG. 80 (a), when the moving trajectory of the wheel B is a vertical line Z passing through the center Qk of the rotating shaft or when it is a vertical line ZZ not passing through the center Qk of the rotating shaft, the cam wheel Even if B is a track ZZZ that can freely move on the sliding surface of the cam body, if a constant force continues to act on the cam wheel B, the cam wheel B can be moved with a constant end force.
If the cam wheel B is at an arbitrary position on the involute vortex line K, the involute vortex line K rotates at a constant rotational force so that the constant force is applied to the wheel B while moving away from the center Qk of the rotating shaft. Can be moved to.
Even when the cam wheel B in FIG. 37 revolves around the rotating shaft Qj of the cam wheel rotating body or the cam wheel B in FIG. 80 moves up and down linearly, the involute vortex line whose shape is determined by the size of the virtual circle is determined. Show the same performance.

FIG. 80A illustrates the case where gravity acts on the cam wheel B. The case where the cam wheel B is moved by the rotation of the involute vortex will be described. Gravity works in parallel on the vertical line Z.
The “force Fb that the wheel presses the sliding surface” is a straight line T passing through the rotation axis Ib of the wheel and “the contact point b between the wheel and the sliding surface”, and is in contact with the virtual circle Ra at the contact point a.
As shown in FIG. 80 (a), unlike the direction of the force Fb acting on the rotation axis Ib of the wheel and the direction of gravity, the intersection angle Θf between the force Fb acting on the wheel and the direction of gravity Z indicates that the moving trajectory of the wheel B is the rotation axis. When the cam wheel B is a trajectory ZZZ that can freely move on the sliding surface of the cam body, whether it is a vertical line Z passing through the center Qk of the shaft or a vertical line ZZ not passing through the center Qk of the rotating shaft However, it changes with the movement of the cam wheel B, and the ratio between the force Fb and the gravity is different. That is, the force Fb changes as the cam wheel B moves, and the rotational force acting around the cam body rotation axis Qk changes and is not constant.

As shown in FIG. 80 (a), when the trajectory of the wheel B is a constant tangent line T03 that is in contact with a fixed point a03 on the virtual circle Ra, the intersection angle Θf between the force Fb and the direction of gravity Z is constant. Yes, the ratio between the force Fb and gravity is constant, the force Fb is constant, and the rotational force acting around the cam body rotation axis Qk is constant.
If a constant rotational force continues to work around the cam body rotation axis Qk, a constant force continues to act on the cam wheel B. Throughout the entire process of moving the cam wheel B, stopping the cam wheel B with a constant force means that the maximum value of the force required to move the cam wheel B is the smallest.

When the trajectory of the wheel B is a constant tangent line T03, the tangent line of the sliding surface K in the “contact point b between the wheel and the sliding surface” is always perpendicular to the constant tangent line T03. Translate.
That is, when the plane contacting the cam body sliding surface moves in parallel with the rotation of the cam body sliding surface, the force acting on the plane on which the cam body sliding surface moves in parallel is constant.
When the plane in contact with the cam body sliding surface is fixed, the cam body rotation axis Qk moves with the rotation of the cam body sliding surface and the distance from the plane changes, but the contact point between the cam body sliding surface and the plane Is a fixed point on the plane without moving, and the cam body rotation axis Qk moves at a certain distance from the perpendicular line set at the fixed point.
When the plane is a horizontal plane, the force Fb and the direction of gravity are parallel and vertical, the line of action of the force Fb coincides with the cam body rotation axis Qk perpendicular to the fixed point, and the cam body rotation axis Qk. Moves on one vertical line.

34 to 36 show rotation transmission means in which the sliding surface K presses the cam wheel to transmit a constant rotational force to the cam wheel rotating body Jq. The constant rotational force of the cam wheel rotating body Jq is a sliding surface. It is also a compression means for converting to a constant pressing force of K. 37 and 80 are rotation transmission means for the cam wheel to press the cam body and transmit a constant rotational force to the cam body, and also a means for moving the cam wheel B up and down by the constant rotational force of the cam body. .
34 to 37, the gradient of the cam body sliding surface with respect to the moving direction of the cam wheel on the cam body sliding surface is constant, but in the case of FIG. 37, the gradient is the cam body as shown in FIG. The smaller the distance from the rotation axis, the smaller.

As shown in FIG. 80 (a), when the moving trajectory of the wheel B is a fixed tangent line T03 that is in contact with the fixed point a03 on the virtual circle Ra, the sliding in the vicinity of the “contact point b03 between the wheel and the sliding surface”. The shape of the surface K is an arc centered on the fixed point a03, and the radius of curvature of the arc increases and becomes gentler as the distance from the cam body rotation axis Qk increases.
The further away from the rotating shaft of the cam body, the greater the “force Fb that the wheel presses the sliding surface” acts, and the wheel becomes difficult to move. The wheel becomes easy to move when a strong force works, and the cam body is rotated.
The farther away from the rotation axis of the cam body, the more the wheel moves, and even if the cam body rotates greatly, the wheel slightly moves in the direction away from the cam body rotation axis Qk. As the cam wheel approaches the rotation axis of the cam body, the cam body rotates faster.
34 to 37, the force acting between the cam body and the wheel is characterized in that the cam body can rotate with a slight circumferential force even when a large force is exerted in the radial direction, and the wheel has pressed the cam body greatly. But the force to rotate the cam body is small. Even when a large weight acts on the wheel as shown in FIG. 80, the wheel can be moved with a small force.
FIG. 80 is a general means using a rotary motion as the vertical movement means, and can move an object up and down with a constant rotational force from the beginning to the end. By making the force acting from the beginning to the end uniform, the heavy object can be moved up and down with the weakest force.

The drawing of involute vortex lines will be described.
As shown in FIG. 80 (a), when the cam wheel B moves on the vertical line Z, the cam wheel B and the sliding surface K near the contact point bi (i = 0.1.2...) The shape of the sliding surface K is an arc Ri (i = 0.1.2 ....), and FIG. 80 (b) shows the starting point bi of the arc Ri (i = 0.1.2 ....). (I = 0.1.2...) Is rotated about the point Qk and arranged on a straight line in the radial direction.
The intersection of the circle Roi (i = 0, 1, 2,...) Centered on the point Qk and the trajectory along which the cam wheels move is a point bi (i = 0, 1, 2,...), And the straight line Ti. (I = 0, 1, 2,...) Passes through the point bi (i = 0, 1, 2,...) And touches the virtual circle Ra at the contact point ai (i = 0, 1, 2,...). . The intersection of the arc Ri (i = 0, 1, 2,...) With the radius centered at the point ai and the circle Roi−1 is ci (i = 0.1.2 ....). is there.
In both FIG. 37 (b) and FIG. 80 (b), the arc bici is congruent at any position on the circle Roi where “the point bi at the intersection of the circle Ri and the trajectory along which the cam wheel moves” is located. . The arc Ri shown in FIG. 37 (b) and the arc Ri shown in FIG. 80 (b) are congruent.

The figure aibici (i = 0.1.2 ...) is rotated around the point O, and the end point ci of the figure aibici is moved to the position of the start point bi-1 of the figure ai-1bi-1c-1i The circular arc bici is continued to the circular arc bi-1ci-1. In this way, the vortex lines b0k1k2k3... Are drawn by making the end point of the next arc continue to the start point of the immediately preceding arc.
In addition, an arc kiki + 1 is drawn that touches the virtual circle Ra at a point ji and has a length jiki as a radius around the point ji, and passes through the end point ki + 1 to the end point ki + 1 farther from the virtual circle Ra. The tangent line Ti + 1 tangent to the point ji + 1 and the length ji + 1 iki + 1 is the radius, and the arc ki + 1 having the same length as the arc ki + 1 is connected sequentially. As a result, vortex lines b0k1, k2, k3... Are drawn.
Since the arcs bici defined by the point bi anywhere on the circle Ri are all congruent, the vortex lines b0k1k2k3... Drawn by rotating and continuing the arc bici are what the cam wheels move. Even so, it is decided to be one.

81 is an embodiment of the rotating mechanism described in FIGS. 23 and 36, and FIG. 82 is an embodiment of the rotating mechanism described in FIGS. 24 and 35, and is a plan view for explaining the operation from fully open to fully closed. .
FIGS. 81 and 82 differ from the embodiment in which the wheel B stays in the vicinity of the door pivot O in the “(A) range” and suddenly moves away from the vicinity of the door pivot O in the “switching range” as shown in FIG. The wheel B rotates relative to the door D. In FIG. 81 (a), wheel B revolves around the pivot axis O of the door together with the door in FIG. 81 (a), and in FIG. 81 (b), wheel B stops and door D rotates. If you change the, the door stops and the wheels are revolving. That is, the rotation angle of the wheel and the rotation angle of the door coincide with each other. In the case of FIG. 57, the rotation angle of the wheel does not coincide with the rotation rotation angle of the door.
In the case of FIG. 81 and FIG. 82 where the wheel B stays on the sliding surface K and moves in the “switching range” in the “(range)” in the case of FIG. 57, the wheel B is in the “(range)”. While moving on the sliding surface K, it stops at the “switching range”. In the case of FIG. 57, the sliding surface K rotates little in the “(range)” and greatly rotates in the “switching range”. In the case of FIGS. ”Rotate further.

In Patent Document 10, as shown in FIGS. 81 and 82, “(range)” is shown. In FIG. 81 (a), the wheel B revolves around the pivot axis O of the door together with the door. Depending on the position on the sliding surface K, the “distance Lf between the force action line F and the center of rotation” is set to a desired value. 81 and 82, the distance Lf is merely made small and constant, but there is a technical difference.
Regardless of the revolution radius of the wheel, the force action line Fb is as close as possible to the center of rotation O, so that the spring force can be reduced to a small size, and the device can be stored if the large spring force necessary for sealing is preserved. The playing box can be designed small.
FIG. 81 (a) is a diagram in which a wheel B is mounted on a connecting shaft C provided on a door D, and a sliding surface K which is an outer edge portion of a cam body KK (not shown) is centered on a fixed support shaft Sw provided on a door frame W. The door D rotates in the direction indicated by the arrow B in the figure as it rotates in the direction indicated by the middle arrow A and the sliding surface K moves along the wheel B.
Wheels B1,..., B6 indicate the position of the wheel B that changes every moment from fully closed to fully open, and the wheel rotation axes C1,..., C6 are on a circle Rb centered on the door pivot O. To move. The tangents Fb1,..., Fb6 of the “virtual circle Ra centering on the pivot axis O of the door” passing through the rotation axis C of the wheel are “force Fb that the wheel B presses the sliding surface K” that changes every moment. , Passing through the virtual circle Ra and the contacts a1,..., A6 through the "contacts b1,..., B6 with the wheels B1,. Touch. Sliding surfaces k1,..., K6 indicate the position of the sliding surface K that changes momentarily from fully closed to fully opened, and are rotated around the fixed support shaft Sw so as to be continuous with the sliding surface k1. The sliding surface K1 is drawn. The sliding surface K is substantially linear.
The fully closed door is shown as D0, the sliding surface as K0, and the wheel as B0.

In FIG. 81 (a), when the rotation axis C of the wheel B is fixed and the fixed support shaft Sw revolves around the pivot axis O of the door, the sliding surface K moves around the fixed support shaft Sw in FIG. When rotating in the opposite direction and moving along the wheel B, the fixed support shaft Sw revolves around the door pivot O in the direction opposite to the arrow B in the figure.
In FIG. 81 (b), the wheel B is mounted on the fixed support shaft Sw provided on the door frame W, and the sliding surface K rotates in the direction of the arrow a in FIG. As the surface K moves along the wheel B, the door D rotates in the direction of arrow B in the figure.

In FIG. 81 (b), the wheel B moves along the sliding surface K along with the door closing rotation in the range from fully open to just before closing (A), and gradually rotates the sliding surface K. Approach the center Sw. In both the range (A) and the range (I), the closing device operates at a substantially constant speed with the closing rotation of the door. As shown in FIGS. 57 to 60, the wheel B does not instantaneously move from one end portion of the sliding surface K to the other end portion in the “range from right before closing to the closing time (i)”. Further, as shown in FIGS. 57 to 60, the operation of the closing device is small in the range (A) and is not large in the range (I).
However, in the embodiment of FIG. 81, the “distance Lb between the force Fb at which the wheel presses the sliding surface and the pivot O of the door” in the range (a) is substantially constant, but the range (ii). It suddenly grows when fully closed. In addition, in the range (ii), the sliding surface K rotates significantly around the “center of rotation Sw or C of the sliding surface K”. At this time, the spring of the urging means of the drive unit (not shown) also greatly expands and contracts.
Even if there is a difference in the structure and operation of the device, if the magnitude of the force transmitted to the door and the change over time are the same, there is no difference in the rotational operation of the door. The door using the cam body and each wheel as the driving means can freely set the magnitude of the force transmitted to the door and its temporal change depending on the shape of the sliding surface.

FIG. 82 shows an embodiment in which the rotation axis of the cam wheel B is fixed in FIG. 34, the cam body rotation axis Qk revolves around the cam wheel rotation body rotation axis Qj, and the sliding body KK revolves while rotating.
In FIG. 82, the cam wheel B is mounted on a fixed support shaft Sw provided on the door frame W, the position of the fixed support shaft Sw is fixed, and the cam body rotation axis Qk revolves around the pivot axis O of the door, thereby sliding the body KK. Revolves while spinning. The cam body rotation shaft Qk is a support shaft provided at the tip of the rotation body Jc. The rotation body Jc is rotatably supported around a connection shaft C provided on the door D, and the tension spring V is a sliding body. It is connected to the support shaft Sk of KK and the support shaft Sd of the door. The cam body rotation axis Qk can approach or leave the door surface.

FIG. 82A is a state diagram when fully opened, and the state indicated by the solid line is a state in which the sliding body KK abuts against the contact Gk provided on the door frame W and stops rotating. A state indicated by a broken line is a state in which the door is further opened, and the pulling spring V extends to expand the full opening angle.
FIG. 82 (b) shows a state just before closing, and the wheel B shows a state in which it approaches the cam body rotation axis Qk from the tip of the sliding surface K. FIG. FIG. 82 (c) shows a sealed state.

As shown in FIGS. 82 (a) and 82 (b), when the inertial force attached to the door increases in the process of closing the door, the magnitude of “force required for rotating the door” decreases, and the rotating body Jc and the door D 34, the distance between the cam wheel rotating body Qj and the cam body rotating shaft Qk (the door pivot O in FIG. 82) is reduced as described with reference to FIG. Works small to rotate the pressure door. When the inertial force attached to the door disappears and becomes smaller, the “force required for the rotation of the door” increases, the intersection angle Θa between the rotating body Jc and the door D increases, and the cam wheel rotating body rotation axis Qj and the door The distance to the pivot axis O increases, which greatly affects the rotation of the cam wheel pressing force door.
Thus, there is a large difference in the movement of the wheel between the embodiment of FIGS. 6-8 and the embodiment of FIGS. 34-37, and the embodiment of FIGS. Means ”and“ switching means ”in which the wheel moves greatly. In the embodiments of FIGS. 34 to 37,“ rotating means in the range (a) ”in which the wheel moves greatly and“ switching means ”in which the wheel does not move. Prepare.
However, in both the embodiment of FIGS. 6 to 8 and the embodiment of FIGS. 34 to 37, the “line of action of the force Fb that the wheel B presses the sliding surface K” does not move from the vicinity of the pivot axis O of the door. ”Rotating means” and “switching means” in which the action line moves greatly. Further, the “switching means” has a common point, and the wheel B operates greatly in the embodiments of FIGS. 6 to 8, and the sliding surface K operates greatly in the embodiments of FIGS.
That is, by moving the action line of Fb, “two ranges in which different magnitudes of force act and can be clearly distinguished” are realized, and when the magnitude of the force changes, the driven rotor (door D) is slightly changed. The open / close device (link device) operates greatly with proper rotation.

FIG. 83 shows an embodiment in which the fixed support shaft Sw is removably attached as in FIG. 13, and the tip of the link A is bent in the same manner as in FIGS. Until the body J and the link A are united, the link A and the link AA are kept in a straight line and are not bent, but the connecting shaft PP crosses the straight line Tswc, and the pivot axis O of the door from the straight line Tswc. Invade areas not included.
83 and 84, UV is charged around the connecting shaft P and urges the rotating body J and the link A in the closing direction. A spring (not shown) is loaded around the connecting shaft Sw, and the rotating body J is urged in the direction of the arrow A in the figure about the fixed support shaft Sw. The door D is closed and rotated in the direction of arrow B in the figure. The rotary body J and the link A are operated by the torsion spring UV until the rotary body J and the link A are closed. After the rotary body J and the link A are closed, the rotary body J and the link A are operated by a spring (not shown). That is, the “rotating means in the range (A)” is driven by the torsion spring UV, and the “rotating means in the range (I)” is driven by a spring (not shown).
The “switching means” is, for example, a spring mechanism shown in FIGS.
FIG. 83 (a) shows a state immediately before sealing, FIG. 83 (b) shows a state when sealing, and FIG.

As shown in FIG. 83 (a), the fixed support shaft Sw is attached to the tip of the rotating body Jq, and is mounted around the rotating body rotating shaft Q so as to be revolved. The rotating body Jq is rotatably supported around the rotating body rotation axis Q, and is urged by the torsion spring UVq in the direction of contact with Gq. Until the rotating body J and the link A are united immediately before the closing, the rotating body Jq remains in contact with Gq and is outside the recess KK at the tip of the ratchet claw Rj.
When the rotating body J and the link A rotate as a unit, the rotating body Jq rotates in the direction indicated by the arrow C in the figure, and as shown in FIG. The shaft Sw is included and fixes the fixed support shaft Sw. When the door is opened after sealing, as shown in FIG. 83 (c), the state where the fixed support shaft Sw is contained in the recess KK at the tip of the ratchet claw Rj is maintained, and the state is rotated from the state shown in FIG. 83 (c). When the body Jq further rotates, the rotating body J rotates around the fixed support shaft Sw, so that the fixed support shaft Sw is discharged out of the recess KK.

In FIG. 83 (a), the connecting shaft PP crosses the straight line Tswc and is in a region not including the door pivot O from the straight line Tswc. "Opens and the door rotates in the opening direction. The connecting shaft C is provided with a long hole to prevent the door from rotating in the opening direction.
In this state, the door cannot be closed due to external force. Further, the connecting shaft P is in a region that does not include the door pivot O from the straight line Tswc. In this state, the door cannot be opened due to external force acting on the door. That is, the door cannot be opened or closed.

From the sealed state shown in FIG. 83 (b), the rotating body J is integrated with the link A while maintaining the state in which the fixed support shaft Sw is contained in the recess KK at the tip of the ratchet claw Rj. When rotating in the opposite direction to the arrow A in the figure, the connecting shaft PP can revolve around the fixed support shaft Sw until it reaches a position crossing the straight line Tswc. As shown in FIG. The rotating body J and the link A rotate while being integrated until the support shaft Sw, the connecting shaft PP, and the connecting shaft C are in a straight line. If the fixed shaft Sw, the connecting shaft PP, and the connecting shaft C are in a straight line and the connecting shaft P is in an area that does not include the pivot axis O of the door with the straight line Tswc as a boundary, the door cannot be opened. If the connecting shaft P is in a region including the pivot axis O of the door with the straight line Tswc as a boundary, the rotating body J and the link A are separated from each other, and the door can be opened.
As shown in FIG. 83 (c), if the connecting shaft P is in the region of the fully open side from the straight line Tswc, when the connecting shaft PP moves away from the position of the fixed support shaft Sw as the door is opened, the connecting shaft PP moves the straight line Tswc. Never cross again.

FIG. 84 shows an embodiment in which the connecting shaft C is mounted so as to be able to revolve as in FIG. 13, and is not bent at the tip of the link A as in FIG. Until the link A is integrated, the link A and the link AA are kept in a straight line and are not bent. Accordingly, the connecting shaft PP crosses the straight line Tswc and does not enter the region that does not include the door pivot O from the straight line Tswc. In the case of FIG. 40, similarly to the case where the link AA is urged by the spring, the connecting shaft PP is forcibly moved in parallel with the “closed door surface” by the push spring U charged in the passage body SZ. The straight line Tswc is entered into an area not including the door pivot axis O.
FIG. 84 (a) shows a state in which the axial cores of the two links are forced to be bent by the push spring U and bent immediately before sealing. FIG. 84B is a state diagram immediately before sealing, and FIG. 84C is a state diagram when sealing.

FIG. 84 (a) shows a state in which the rotating body J and the link A are separated from each other, and FIG. .
In FIG. 84 (b), the connecting shaft PP crosses the straight line Tswc and is in a region that does not include the pivot axis O of the door from the straight line Tswc. "Opens and the door rotates in the opening direction. In this state, the door cannot be closed due to external force. The connecting shaft P is in the region including the pivot axis O of the door from the straight line Tswc, and an external force can act on the door to open the door. That is, unlike the door of FIG. 83, there is no problem with opening the door. In FIG. 84 (b), the passage body SZ is prevented from rotating in the direction indicated by the arrow C in the figure and rotating in the door opening direction.

The passage body SZ abuts against the contact Gd and is prevented from rotating in the direction opposite to the arrow C in the figure, and the connecting shaft PP revolves around the fixed support shaft Sw as shown in FIG. Seal.
The axial center line Zaa of the link AA is a straight line passing through the connecting axis PP and the connecting axis C, and the door is opened if the position of the fixed support shaft Sw is not in the region including the pivot axis O of the door from the axial center line Zaa of the link AA. The door cannot be opened if it is in the area including the pivot axis O of the door.
In the case of the door of FIG. 84, unlike the door of FIG. 83, the connecting shaft P is in the region of the fully open side with respect to the straight line Tswc and does not cross the straight line Tswc.
As shown in FIG. 84 (c), the connecting shaft P is in the region of the fully open side with respect to the straight line Tswc, and when the connecting shaft PP moves away from the position of the fixed support shaft Sw as the door is opened, the connecting shaft Pp Never cross again.

In FIG. 9A, when the connecting shaft C, which is a fulcrum of the spring, is in the range (A) with the straight line Ts as a boundary, the door is biased in the closing direction, and when in the range (I), the door is biased in the opening direction. Is done. It is assumed that FIG. 9 is displayed in an XY coordinate system in which the straight lines X and Y are the origin of the pivot axis O of the door and the arrow direction in the drawing is positive. Similarly, all of the drawings in the present application are displayed in a Y coordinate system in which a straight line D0 indicating when the door is fully closed and a straight line D100 indicating when the door is fully open are X-axis, Y-axis, and O is the origin.
When the fixed support shaft Sw moves, the straight line Ts rotates around the origin O, and at the same time, the “range biased in the closing direction” and the “range biased in the opening direction” also rotate. Before and after the fixed support shaft Sw moves, the door opening angle Θd at which the urging direction is switched by the movement of the straight line Ts is different.
While the fully closed door is slightly opened in FIG. 9A, when the fixed support shaft Sw on the upper axis of the straight line D10 moves to the straight line D100 when fully closed, the door is biased in the opening direction. Further, when the fixed support shaft Sw moved on the straight line D100 returns to the position on the straight line D10 while the fully opened door is slightly closed, the door is biased in the closing direction. The fixed support shaft Sw moves while the fully closed door is opened a little, and it opens freely until the door is fully opened. It will be closed without permission.
In the process of closing the door in FIG. 9A, the sealing device works in the range between the straight line D10 and the X axis.

If the fixed support shaft Sw is fixed at a position on the straight line D10 and does not move, the door will open freely if the connecting shaft C crosses the straight line D10 when the door is opened, but the connecting shaft C is straight when the door is closed. If you do not cross D10, the door will not close.
Thus, when the fixed support shaft Sw is fixed and the straight line Ts does not move, it does not open arbitrarily even if it is closed arbitrarily, or it does not close arbitrarily even if it is opened arbitrarily. When the door moves beyond the straight line Ts, the door is urged in the returning direction before the straight line Ts is exceeded, but in the range exceeding the straight line Ts, the door is urged in the going direction. When the stationary door is moved, the force in the direction of returning to the spring is stored.

When the straight line Ts is close to the X axis or the Y axis, the range in which the force is stored in the spring is large in either the return or return direction, and the range in which it rotates freely becomes small.
Even if the position of the straight line Ts is set to such a position that “the range in which the force is stored in the spring is small and the range in which it rotates freely” is set, the spring does not have a force when it is rotated by the spring force. In addition, the straight line Ts is at a position where “the range in which the force is stored in the spring is large and the range in which the spring rotates freely becomes small”.
The “door shown in FIG. 85 and below” is designed so that the range in which the force is stored in the spring is small and the range in which the spring rotates freely is large in either direction or return. We begin by moving the straight line Ts at the beginning of.
“The door shown in FIG. 85 and below” is a movement of the fixed support shaft Sw and “a door that opens freely until it is fully opened while it is slightly opened, and that is closed until it is fully closed while it is slightly closed”. In the opening process, the opening angle of the door that opens freely until the door is fully opened is different from the opening angle of the door that opens freely until the door is fully closed in the closing process.

The “door shown in FIG. 85 and below” is how to handle the work of moving the straight line Ts while accumulating the force on the spring, and the operation until the straight line Ts is exceeded is a problem. Does not matter.
The straight line Ts is a boundary line passing through the pivot axis O of the door, and the urging direction changes depending on which side the door is located with the straight line Ts as a boundary. The means for changing the urging direction is such that the door crosses the straight line Ts at the beginning of the work so that the urging direction changes as the door crosses the straight line Ts.

The door described in FIGS. 85 to 87 is a door that opens freely until it is fully opened when the closed door is opened a little, and is closed automatically until it is fully closed when the door that is fully opened is slightly closed, and the position where the biasing direction is switched is Different doors when opening the door and closing the door. That is,
“A door that reciprocates between a fully open position and a fully closed position, and when the door is opened from the fully closed position, the door is urged in the fully open direction from the fully closed direction. An opening direction switching means for switching, and a closing direction switching means for switching a state to be biased in a fully closing direction from a state biased in the fully opening direction when the door is closed from the fully opened position, the opening direction switching means The door is characterized in that the opening angle of the door when operating is different from the opening angle of the door when the closing direction switching means operates. "
The urging direction of this door is switched by moving the fixed support shaft located near the driven shaft of the switchgear according to the present invention, or by moving the sliding surface, or by switching the rotation direction of the link of the switchgear. It is a door.
As shown in FIG. 85 and the following, the switching means provided in this door is “a rotating body that is rotatably supported around a rotating body rotating shaft and is urged by a toggle spring so as to reciprocate between two stationary positions. The rotating body moves from one of the stationary positions to the other at a position where the opening direction switching means operates and a position where the closing direction switching means operates.
“A rotating body that swings between a position that is urged by a toggle spring and is urged in the fully closed direction and a position that is urged in the fully opened direction and that is stationary in the fully opened direction, The rotating body is connected to the means for urging the door, and the rotator is attached to the door when switching from one of the state of being urged in the fully closing direction and the state of being urged in the fully opening direction. The door according to claim 15, wherein the biasing direction of the biasing means is reversed. Switching means for switching freely by the rotation of the door, and by linking this to the opening / closing device of the present invention, the urging direction of the door is switched.

When the door is rotated by the tensile force of the closing device, the door moves toward the straight line Ts, and when the door is rotated by the compression force of the closing device, the door moves away from the straight line Ts. When the door is rotated by the pulling force of the closing device, the distance between the “mounting shaft with the fixed part” and the “mounting shaft with the driven body” moves toward the position where the minimum value is reached. When the door is rotated by the compressive force, the distance moves away from the position where the maximum value is shown.
As shown in FIGS. 9 and 64, the position indicating the minimum value or the position indicating the maximum value is when both are on a straight line passing through the pivot axis O of the door, and at this time, both are closest. Therefore, the straight line Ts is a boundary line passing through the pivot axis O of the door.
The attachment shaft at the end of the closing device has an attachment shaft for the fixed portion and an attachment shaft for the driven body, one of which rotates around the pivot axis O of the door and the other is fixed. The other passing point other than the pivot O is an attachment shaft at the end of the closing device, which is the side on which the position is fixed. As shown in FIGS. 64 (c) and 64 (d), when the fixed mounting shaft is far from the pivot axis O of the door, it is necessary to move the straight line Ts to move the straight line Ts. In this case, the closing device switches the direction of the force acting on the door. When the means wp for moving the mounting shaft is adopted, the straight shaft Ts is moved by moving the support shaft closer to the pivot axis O of the door.

Further, a toggle spring is used as means for stopping the straight line Ts at the position after the movement. The force to rotate the door is small and there is no force to pull the toggle spring back. Therefore, the work for storing the force in the spring at the beginning of the work is the rotation of the toggle spring.
The toggle spring is rotated in a small range at both ends of the rotation range, but it is disabled when returning to the end at both ends of the rotation range, and is a one-way operation switching device that works only when starting work. There must be.
The means for switching the urging direction includes a means for changing the urging direction of the spring, and there is a method of reversing the rotation direction of the apparatus without moving the mounting shaft. Since the tension spring cannot be replaced with a push spring, the drive spring is a toggle spring. In this case as well, the urging direction is switched by a toggle spring, and the mechanism is the same.

In the case of FIGS. 1, 9, and 10, it is switched by the movement of the fixed support shaft Sw. Alternatively, it is switched by changing the biasing direction of the spring. In the case of FIGS. 3 and 4, the movement is switched by the movement of the movement support shaft Sj. That is, the urging direction changes depending on which side of the door the moving support shaft Sj is fixed.
When the attachment part of the switchgear is a wheel and a sliding surface, the slope of the sliding surface is switched to move the position where the wheel stays in “(A) range”. In the case of FIGS. 3 and 4, switching is performed by switching the gradient of the sliding surface. Whether the mounting portion of the switchgear is a wheel and a sliding surface or a fixed support shaft, the action point is fixed at a position close to the pivot axis O of the door. This is the same in that it reciprocates the stationary position of the location.
As shown in FIG. 57, the switching means is not simple for an apparatus in which the wheel and the sliding surface move greatly in relation to both the “(A) range” and the “(I) range”. As shown in FIGS. 10 to 12, when the wheel and the sliding surface are not related to both “(A) range” and “(A) range”, switching means may be taken for “(A) range”. I can do it.

The switching means attaches a toggle spring to a rotating body provided with a rotating shaft near the pivot of the door and maintains two stationary states. The rotating body J shown in FIGS. The position of the mounting shaft and the gradient of the sliding surface are switched. Further, when the urging direction and the rotation direction are switched or when the moving support shaft is moved, the position away from the door pivot O and the switching means are linked.
85 and 86 are means for directly attaching the fixed support shaft and the sliding surface to the rotating body J and rotating them.

The position of the fixed support shaft Sw in the case where the fixed support shaft Sw is provided in the vicinity of the door pivot O of the door frame W and the connecting shaft C provided on the door is connected by a connecting material and a tensile force acts on the connecting material. FIG. 85 shows an example of a rotating mechanism for moving the lens.
The switching rotator JB is rotatably supported around a switching rotator rotating shaft Qb provided on the door frame W, and swings between G1 and G2 by a toggle spring, and abuts against G1 and G2 at two locations. At rest. Further, a wheel B is mounted on a rotating shaft Ib of a wheel provided at an intermediate portion, and a fixed support shaft Sw is provided at a tip portion. The fixed support shaft Sw is in the position of Sw1 when the switching rotator JB comes into contact with G1 and stops and is in the position of Sw3 when it comes into contact with G2 and stops and the wheel B moves slightly. Move a lot.
The tension spring V has one fulcrum attached to the intermediate shaft of the switching rotator JB, and the other fulcrum attached to the shaft Sv provided on the door frame W. Qb is provided. The straight line Ts is a straight line passing through the support shaft Sv and the switching rotator rotation axis Qb. When the switching rotator JB crosses the straight line Ts, the axis of the pulling spring V is crossed, and the switching rotator JB hits G1 and G2. Move to either one of them.

The means to move the fixed support shaft Sw from the Sw1 position to the Sw2 position while opening the fully closed door is "Check valve Go that works when opening the door". The means for moving the support shaft Sw from the position of Sw3 to the position of Sw2 is a “check valve Gs that works when the door is closed”, each of which rotates about the connecting shafts Co and Cs provided on the door, The springs (not shown) are biased around the connection shafts Co and Cs so as to be stationary at a certain angle with respect to the door surface. 85A shows the state where the check valve Go is stationary at a certain angle with the door surface, and Θs shows the state where the check valve Gs is stationary at a certain angle with the door surface in FIG. 85C. Show.
85 (a) and 85 (b) are explanatory views of the operation of “the check valve Go that works when the door is opened”, and FIGS. 85 (c) and 85 (d) are the operations of the “check valve Gs that works when the door is closed”. It is explanatory drawing.

FIG. 85 (a) is an operation explanatory diagram when the fixed support shaft Sw is at the position of Sw1 and is stationary, and the door is closed in the direction indicated by the arrow B in the figure. Shows a state of passing around the wheel B without acting on the wheel B.
The check valve Go has sliding surfaces Ko1 and Ko2, and the sliding surface Ko1 moves along the “wheel B at the position of Sw1,” while the check valve Go15 rotates in the direction opposite to the arrow a in the figure. Detour around wheel B. The check valve Go0 includes the wheel B on the sliding surface Ko2 while rotating in the direction of arrow A in the figure by a spring (not shown).
FIG. 85 (b) shows that the “check valve Go that works when the door is opened” presses the wheel B included in the sliding surface Ko2 while switching the fully closed door slightly in the direction of the arrow D in FIG. The body JB rotates in the direction of the arrow C in the figure, the fixed support shaft Sw moves from the position of Sw1 to the position of Sw2, and after passing through the position of Sw2, the state moves to the position of Sw3 without permission. The door opening angle Θdo shown in the figure indicates the door opening angle Θd when the door is freely rotated in the opening direction.

As shown in FIG. 85 (c), when the fixed support shaft Sw moves to the position of Sw3 and stops, the door rotates in the direction to open freely, and “the check valve Gs that works when closing the door” is the wheel B. Passes around the wheel B without acting on. The check valve Gs has sliding surfaces KS1 and Ks2, the sliding surface Ks1 moves along “wheel B at the position of Sw3”, and the check valve Gs60 rotates in the direction opposite to the arrow e in the figure. Detour around wheel B. The check valve Gs90 includes the wheel B on the sliding surface Ks2 while rotating in the direction of arrow E in the figure by a spring (not shown).
FIG. 85 (d) shows a state in which “the check valve Gs that works when the door is closed” presses the wheel B contained in the sliding surface Ks2 while the door that is fully opened is slightly closed, and the switching rotator JB moves to the arrow in the figure. FIG. 6 is an operation explanatory diagram of rotating in the direction, the fixed support shaft Sw moves from the position of Sw3 to the position of Sw2, and moves to the position of Sw1 without permission after passing the position of Sw2.
The door opening angle Θds shown in the figure indicates the door opening angle Θd when the door rotates without permission. The feature of this door is that the door opening angle Θd differs between “when the door automatically rotates in the opening direction” and “when the door rotates freely”.

`` Check valve Go that works when opening the door '' is a means to move the fixed support shaft Sw so that the door rotates in the opening direction while opening the fully closed door a little. The "non-return valve Gs that works when closing the door" does not act on the fixed support shaft Sw when it is closed, and the fixed support shaft Sw is rotated so that the door closes while the door is fully opened. The moving means does not act on the fixed support shaft Sw after moving and when opening the door.

FIG. 86 is an operation explanatory view of the urging direction switching device, and FIG. 86 (a) is an operation explanatory view for explaining a process from opening a little from the fully closed state to the door fully opening after that. The rotator J1 is rotatably supported around the rotator rotation axis Q, and rotates in the direction of the arrow A in the figure around the rotator rotation axis Q. The connecting shaft C is provided at the tip of the rotating body J1, and the link AA is rotatably supported around the connecting shaft C.
The arc Rq is a circumference centered on the rotating body rotation axis Q, and the connection axis C moves along the circle Rq in the direction of arrow A in the figure. C1, C2,... C5 indicate the respective positions of the connecting shaft C when the rotating body J is at the positions J1, J2,.
The link A is rotatably supported around the fixed support shaft Sw, is urged by a toggle spring VV, and abuts against the contact G1 and the contact G5 to maintain a stationary state.
A connecting shaft P is provided at the tip of the link A, and a connecting shaft Pa is provided at the tip of the link AA.

FIG. 86A shows a process in which the link A hits G5 and remains stationary, and the link AA revolves around the rotating body rotation axis Q as the rotating body J rotates. AA1, AA2, AA3,... AA5 indicate the positions of the links AA when the rotating body J is at the positions of J1, J2, J3,. A state in which the shaft Pa is engaged with the connecting shaft P at the tip end of the link A is indicated by a solid line in 86 (a).
AA1 shows a state in which the link AA is separated from the sliding surface K, AA2 shows a state in which the side surface of the link AA is in contact with the sliding surface K, and AA3 shows a state in which the link AA moves along the sliding surface K. AA4 is the moment when the link AA4 is about to leave the sliding surface K.
Rc4 is a circumference centered at the point C4. The link AA4 moves away from the sliding surface K and rotates around the connection axis C4 in the direction indicated by the arrow C in the figure. It contacts the connecting shaft P at the tip.

FIG. 86 (b) is a state diagram in which the rotating body J rotates in the direction opposite to the arrow A in the figure, and is an operation explanatory diagram for explaining the process from the fully open state to the door closing without permission after that.
AA5 indicated by a one-dot chain line in FIG. 86 (b) is AA5 indicated by a solid line in FIG. 86 (a), and the state shown by the solid line in FIG. 86 (b) is maintained while the connecting shaft P and Pa are engaged. Migrate to
The link A indicated by the solid line in FIG. 86 (a) is urged by the toggle spring VV and is in contact with G5.
When the rotating body J moves from the position of J5 to the position of J6 from the state shown by the solid line in FIG. 86 (a), it moves along the circle Rsw in the direction of arrow D in the figure while the connecting shaft P and Pa are engaged. When the tip of the link A crosses the axial center line Zv of the toggle spring VV, the urging direction of the toggle spring VV is switched, and the link A rotates freely until it comes away from the hit G5 and comes into contact with the hit G1. The engagement between the tip end of the link A and the tip end of the link AA is released.

That is, the link A rotates greatly by a slight rotation when the rotating body J is started. By this rotation, the mounting shaft of the present invention can be moved. At the stage where the door starts to rotate slightly, the biasing direction of the door is switched.
The above-described operation of the urging direction switching device of FIG. 86 passes at the end or start point of the door rotation without acting on the urging means that is waiting, and switches the unidirectional operation that starts when starting in the reverse direction. As shown in FIG. 85, the discriminating means using a check valve is omitted as in the urging direction switching device of FIG.

Rc6 is a circumference centered at the point C6. As shown by AA6, the connecting shaft Pa at the tip end of the link AA is separated from the connecting shaft P at the tip end of the link A, and around the connecting axis C6 in the direction of arrow C in the figure. The link AA moves on the track Rc6 in the direction indicated by the arrow C in the figure, and the link AA moves to the position AA7. In AA8, the rotating body J further rotates to close the link AA. The contact state is shown. AA9 shows a state in which the link AA moves along the sliding surface K. The direction of AA9 shown in FIG. 86 (b) is different from that of AA3 shown in FIG. 86 (a).
AA10 is in a state where the link AA is about to leave the sliding surface K. At this time, the link A is already in contact with G1 and is waiting at the position of A1.
The subsequent operation is the same as the operation described with reference to FIG. 86A, and AA4 shown in FIG. 86A is symmetrical to AA10 shown in FIG. 86B. The connecting shaft Pa at the front end of the link AA moves in the direction of the arrow in the figure along the circle Rc10 and comes into contact with the connecting shaft P at the front end of the link A that is on standby.

FIG. 87 is a diagram for explaining the operation of the switching means for the biasing direction of the spring of the drive unit. FIGS. ) (D) shows a process in which the biasing direction of the spring is switched slightly after the fully closed state. 87 (a) and 87 (c) show the beginning of the switching means, and FIGS. 87 (b) and 87 (d) show the state at the end of the switching means.
The arrow in the figure indicates the direction of rotation of the door. The rotating body J is rotatably supported around a connecting shaft C provided on the door D, and a supporting shaft for attaching a wheel B to one end and attaching a spring to the other is provided.
The rotating body JJ is rotatably supported around a connecting shaft C provided on the door D, and the link A is connected to the connecting shaft P at the other end. The link A is rotatably supported around the fixed support shaft Sw.
The ratchet claws G90 and G0 are rotatably supported around the rotation support shafts I90 and I0, respectively, and are urged by a spring (not shown) so as to return to the state shown in the drawing.

The rotating body J reciprocates between a stationary state shown in FIGS. 87 (a) and 87 (d) and a stationary state shown in FIGS. 87 (b) and 87 (c). In FIGS. 87 (a) and 87 (d), a tensile force acts on the link A and the link A is rotated in the opening direction. In FIG. 87 (d), the urging direction is switched to the opening direction, and the rotating body J revolves while remaining stationary and shifts to the state shown in FIG. 87 (a).
In FIG. 87 (b), a compressive force acts on the acting body, in FIG. 87 (c), a compressive force acts on the acting body, and in FIG. 87 (d), a tensile force acts on the acting body. In FIG. 87, the wheel B is included in the ratchet pawl G90, and when the door rotates in the direction of the arrow in the figure, the state shown in FIG. 87 (b) is obtained. Move the axis. When the wheel B is further rotated so that the wheel B moves away from the ratchet pawl G90, the door rotates freely and moves to the state shown in FIG. 87 (c). When the door is opened as shown in FIG. 87 (d) including the ratchet pawl G0 wheel Bw, the rotating body J rotates in the direction opposite to the arrow a in the figure to move the support shaft to the spring. When the wheel B is further rotated in the opening direction and the wheel B comes away from the ratchet pawl G0, the door rotates freely and moves to the state shown in FIG. 87 (a). The position is different between the end of the switching means shown in FIG. 87 (b) and the end of the switching means shown in FIG. 87 (d).

The opening / closing body that rotates around the rotation axis can be roughly divided into a door with the rotation axis being vertical and a lid when it is horizontal. The former and the latter swing between the fully open position and the fully closed position. In order to pass a person or an object, rotation in the reverse direction is prevented between the fully open position and the fully closed position. There is a difference between the former and the latter in whether the center of gravity moves in the vertical direction. In the former, the rotational resistance of the rotating shaft is constant throughout the rotation of the door, and the door rotates even if little force is applied. However, the latter requires that the center of gravity moves not only in the vertical direction but also in the horizontal direction as the lid rotates, so that the lid does not drop, and the rotational force acting on the rotation axis of the lid changes.
As described above, the former and the latter have a difference in whether the rotational force acting on the opening / closing body is constant or changes in the range between the fully open position and the fully closed position. Or the force which latches a lid | cover works, and it is the same in the point from which the force from which a magnitude | size differs from the rotational force which acts on the opening / closing body until then works.
In the former, the constant rotational force is always balanced against the constant rotational resistance so that the rotational speed of the door does not accelerate, and the latter is always balanced while changing the rotational force against the varying rotational resistance. The former and the latter rotation mechanisms are the same because the forces are balanced in the middle of the rotation, and different forces are applied at the beginning or end of the rotation.

88 to 92 use the gravity of the weight instead of the spring as the rotation urging means of the door. The door and the weight are connected by a string, and the pulley is inserted in the middle of the vertical movement of the natural fall of the weight. Thus, it is converted into “rotation of the door about the vertical rotation axis” or “rotation of the lid about the horizontal rotation axis”. When the spring is used as the biasing means, the spring expands and contracts with the rotation of the door to reduce the force. However, when the weight gravity is used as the biasing means, the gravity is constant regardless of the height at which the weight falls. The force for biasing the door does not decrease with the rotation of the door and is constant.

FIG. 88 is an elevational view illustrating the operation of “means for decelerating the door” just before closing, which is divided into a case where the door is opened wide and the hand is released and a case where the door is opened slightly and the hand is released from the handle. handle. Thus, the brake is applied only when the inertial force is attached just before the closing, and the brake is not applied when the inertial force is not attached.
Applying the brakes means reducing the negative force, meaning that there is not enough power to rotate the door due to insufficient power to close the door. The door will be stopped at the position where the brake is applied, but the present invention will continue to operate even when the brake is applied so hard that the door stops, and the "door closer with a hydraulic cylinder" In order to prevent the door from stopping like this, the spring strength is not set to “force exceeding the brake strength”.
In the present invention, by applying a brake, even if the force to close the door is insufficient, the spring strength remains weak and the opening / closing device continues to operate. Absent.

The structure of the slider moving device shown in FIG. 88 will be described.
The slider D reciprocates between the start point K1 and the end point K2 of the passage K, and the movement of the slider D is a means for rotating the revolving door or moving the sliding door linearly.
A link A is rotatably supported on a connecting shaft C provided on the slider D. A wheel rotating shaft Ib is provided at the tip of the link A, a wheel B is mounted on the wheel rotating shaft Ib, and the string Sc One end is mounted. A weight W1 is attached to the other end of the string Sc, and a weight W2 is attached to the middle of the string Sc. The middle of the string Sc moves along the pulley Bk. The sliding surface KK is rotatably supported around the support shaft Ik, is urged in the direction of the arrow C in the figure by its own weight, and is stationary in a state where it abuts against the contact G.

When the weight W1 that moves up and down and the slider D are connected by the string Sc via the pulley Bk and the slider D is moved by the weight of the weight W1, the force that pulls the slider D does not change depending on the position of the weight W1. The weight of the weight W1 is a force when the stationary slider D starts to move, and is a force that is slightly larger than the maximum static friction force acting on the stationary slider D and is smaller than the force that presses the moving body toward the end point K2. is there.
In the case where the slider D moves as shown in FIG. 88C, the force with which the slider D to which the inertial force is attached presses the end point K2 is greater than the force with which the stationary slider D presses the end point K2. The weight W2 gets over the pulley Bk and moves from the horizontal movement to the falling movement, and the weight W2 is added to the weight W1, and the slider D is moved. 88 (b) to 88 (f), the weight W1 is not shown.

The operation of the slider moving device of FIG. 88 will be described.
88 (a) to 88 (c) are explanatory diagrams of "rotating means in the range of (A)" and illustrate a process of sealing the door by widely opening the door and releasing the handle. FIG. 88 (a) shows a state in which the weight W1 falls in the direction of arrow A in the figure and the slider D moves through the passage K in the direction of arrow B in the figure. The force with which the weight of the weight W1 pulls the slider D is the maximum static friction force acting on the slider D. FIG. 88 (b) shows a state in which the wheel B rides on the upper surface of the sliding surface KK just before closing and moves along the upward gradient KK1.
The frictional force acting on the slider D that has started to move is smaller than the maximum static frictional force due to the kinetic frictional force, and when the slider D that has started to move is pulled by the weight of the weight W1, more force than necessary is continuously applied. Is accelerated. As shown in FIG. 88 (b), even if the wheel B rides on the upper surface of the sliding surface KK and a part of the force pulling the slider D is supported and reduced by the ascending slope KK1, the wheel B remains in the ascending slope KK1. Do not stay on top. At the same time, as the wheel B rises up the slope KK1, the slider D whose moving speed is accelerated due to the gradually increasing inertial force is decelerated.

88 (b) to 88 (c) are explanatory diagrams of the “switching means”, and FIG. 88 (b) shows a state in which the wheel B that has fully climbed the gradient KK1 is about to leave the sliding surface KK. (C) shows a state in which the wheel B has fallen away from the sliding surface KK. At the same time, the weight W2 gets over the pulley Bk and falls, and the weight of the weight W2 pulls the slider D.
In the process of FIGS. 88B to 88C, the weight load is increased with little movement of the slider D. As described above, the opening / closing device of FIG. 88 also includes “switching means” for switching from “rotating means in range (A)” to “rotating means in range (I)” with little movement of slider D. Yes. This prevents the slider D from accelerating as much as possible even if a large force of the weight W2 acts before the closing.

88 (d) to 88 (f) illustrate the process of opening the closed door, and FIG. 88 (d) shows a weight not shown in FIG. 88 (d) as the slider D moves 1 in the direction opposite to the arrow B in the figure. W1 is pulled up 2 in the direction opposite to the arrow A in the figure, and the wheel B moves under the sliding surface KK and moves 4 while jumping 4 up the sliding surface KK in the direction opposite to the arrow C in the figure.
FIG. 88 (e) shows a state where the wheel B is about to dive through the lower surface of the sliding surface KK. FIG. 88 (f) shows a state where the wheel B has passed through the lower surface of the sliding surface KK and the slider D has reached the starting point K1. The sliding surface KK rotates around the support shaft Ik in the direction of the arrow C in the drawing and comes into contact with G.

88 (d) and (e) illustrate the case where the door is slightly opened and the hand is released from the handle. The wheel B moves along the lower surface of the sliding surface KK, and the wheel as shown in FIG. 88 (b). B moves linearly without rising, and the weight of the weight W1 pulls the slider D without losing a part of the force as shown in FIG. 88 (b) and starts moving the stationary slider D. To do. Thereafter, the weight of the weight W2 is added to the weight of the weight W1, and the slider D is pulled. In this way, the state shown in FIG. 88 (b) is obtained, and the door is sealed. In this way, in the process of opening the door, the door will not remain stationary wherever the hand is removed from the handle.
Further, in the process of closing the door, even if the weight W1 is insufficient to pull the slider D, if the door continues to move due to the inertial force of the door, the door does not remain stopped and is always sealed. The door works to dent the latch halfway before it is sealed. When the door is in contact with the latch, the force to dent the latch in motion is less than the force to dent the latch in a stationary state, so unless you release your hand in contact with the latch, the door Since the inertia force is not lost, the door is surely sealed even if the weight W1 and the weight W2 are less than the force for sealing the door. As described above, the weight of the weight W1 and the weight of the weight W2 may be set to “force that causes the latch to be depressed in a stationary state”, and the slider D may be strongly pressed against the end point K2, but inertial force is used. Therefore, it is desirable to set a small force for sealing the door, and no force is required to open the closed door.

FIG. 89 is an operation explanatory elevation view for explaining the operation of the opening / closing device of the canopy D attached to the ceiling. The rotation axis of the canopy D is horizontal, and the center of gravity of the canopy D moves both in the vertical direction and in the horizontal direction, but the rotation mechanism in FIG. 89 is not only used when the rotation axis is horizontal, It is also used when it is vertical.
89 (a) shows a fully opened state with the canopy D suspended vertically, FIG. 89 (b) shows a state just before the canopy D is closed, and FIG. 89 (c) shows a horizontal state with the canopy D closed. It shows the state.
The sliding body KK has a concave sliding surface K, and is provided with a connecting shaft PP at an end near the canopy D, and one end of the link A is connected to this. The other end of the link A is attached to a connecting shaft C provided on the canopy D. A connecting shaft P is provided at the end of the sliding body KK far from the canopy D, and one end of the string Sc is connected to the connecting shaft P. The counterweight W at the other end of the string Sc is attached. The string Sc moves along the fixed pulley Bc and pulls the connecting shaft P by the vertical movement of the counterweight W.
The pivot axis O of the canopy D, the rotation axis Ib of the wheel B, and the rotation axis Sw of the fixed pulley Bc are rotation axes provided on a fixed portion that is attached to the ceiling surface, and the connection axis C is a rotation axis provided on the canopy D. Is horizontal.

In the “range from fully open to just before closing (A)” from the state shown in FIG. 89A to the state shown in FIG. The contact b "between the wheel B and the sliding surface K" is hardly moved. In the operation shown in FIG. 89 (a), the sliding body KK functions as a crank and the link A functions as a connecting rod. The circular motion of KK is changed to the linear reciprocating motion of link A.
It differs from Patent Document 5 in that the rotation direction around the pivot axis O of the canopy D and the rotation direction around the “rotation axis Ib of the wheel B” of the sliding body KK are the same. This is different from Patent Document 6 in that the link A is inserted between the canopy D and the sliding body KK. Due to this difference, by increasing the “distance Lfc between the force action line Fc and the rotation center Ib”, the rotational force M is transmitted to the driven rotating body D in a small manner “rotating means in the range (A)”. "Rotating means in the range of (i)" that transmits the rotational force M to the driven rotating body D by reducing the distance Lfc, and with little rotation of the driven rotating body D. “Switching means” for switching from “rotating means in range (a)” to “rotating means in range (ii)” becomes possible.

FIG. 89 (a) is an operation explanatory view of the opening Θd of the canopy D from 100 degrees to 45 degrees in the “range from fully open to just before closing (A)”. Is a descriptive view of the releasable restraining means that hardly moves.
The string Sb pulls the connecting shaft P in a direction perpendicular to the moving direction of the wheel B, the “contact point b between the wheel B and the sliding surface K” hardly moves, and the connecting shaft PP is the rotating shaft of the wheel B. Revolve around Ib. The distance between the “contact point b between the wheel B and the sliding surface K” and the connecting shaft PP hardly changes, and the link A also moves in parallel. The value of “distance Lfc between the force acting line Fc acting on the canopy D and the rotation center Ib” is kept large, and the rotational force M acting around the wheel B reduces the force Fc acting on the canopy D. .
The rotational force M acting around the wheel B due to the weight of the canopy D is “the distance between the center of gravity of the canopy D and the pivot axis O” in the state shown by the solid line in FIG. 89A, and the canopy D is closed. However, the distance between the “line of action of the force that the link A pulls the connection axis C” and the wheel rotation axis Ib becomes smaller and rotates while maintaining a balanced state.

As shown in FIG. 89 (b), the restraining means for preventing the "contact point b between the wheel B and the sliding surface K" from moving in the "(A) range" is shown in FIG. 89 (b). The direction of the force pulling the wheel moves from the direction perpendicular to the moving direction of the wheel B to the parallel direction and is released.
Also, a recess into which the wheel fits in the vicinity of the connecting shaft P is provided, or a check portion that engages the wheel is provided in the vicinity of the connecting shaft P to restrain the movement of the wheel, and the wheel is detached from the recess, or the check portion is Get over the wheel to move.
As shown in FIG. 89 (b), the sliding surface K moves along the wheel B without moving the position of the connecting shaft C almost before closing. The link A rotates significantly around the connection axis C. During a right angle, the “contact point b between the wheel B and the sliding surface K” hardly moves.

As shown in FIG. 89 (b), if the shape of the concave surface of the sliding surface K is substantially along the circumference Rc5 centered on the position C5 of the connecting shaft C before the closing dimension and the length of the link A as the radius. The position of the connecting shaft C remains almost unchanged, that is, the state of the canopy D changes from the state of FIG. 89 (b) to the state of FIG. 89 (c) with little rotation. As shown in FIG. 57, the moving track of the wheel does not intersect the sliding surface, and the wheel can move along the sliding surface K. Also in FIG. 89, the wheel restrained in the vicinity of the connecting shaft P moves on the condition that the wheel can move relative to the sliding surface K.
The sliding surface K moves greatly along the wheel B, and the “contact point b between the wheel B and the sliding surface K” moves from the vicinity of the fulcrum of the sliding surface K to the end. That is, in the state of FIG. 89 (b), the distance between the “line of action of the force that the link A pulls the connecting shaft C” and the pivot O is small, and the distance between the center of gravity of the canopy D and the pivot O is large. Before the closing, the force is largely insufficient, and a temporary stop state is entered. Thereafter, the state shifts to the state shown in FIG. 89 (c).

FIG. 89 (c) is a state diagram at the time of sealing. The sliding body KK acts as a lever, the link A is substantially perpendicular to the canopy D, “the contact point b between the wheel B and the sliding surface K” and the connecting shaft PP. The distance between and the connecting shaft PP is small, the distance from the “contact point b between the wheel B and the sliding surface K” to the counterweight W is large, and the string Sc is separated from the pulley Bc. The total weight of the counterweight W is pulled away and the connecting shaft P at the end of the sliding body KK is pulled without being supported by the pulley Sc. Since the force pulling the connecting shaft P at the end of the sliding body KK works in the vertical direction, the sliding body KK is substantially parallel to the canopy D, and the link A is also substantially perpendicular to the canopy D. The force Fb for pressing is also substantially perpendicular to the canopy D, and a strong sealing force is exerted.

The means by which two different forces act on the "rotating means in the range (A)" and the "rotating means in the range (I)" is the "distance between the force action line and the center of rotation". A means for switching from large to small or from small to large and a part of the counterweight W is supported and dispersed on the pulley in the “(A) range” and detached from the support in the “(A) range” Although it is a means to load weight, only one of the two means can exert two different forces. However, both the former and the latter are possible only when the “switching means” is moved largely by moving the connecting shaft P and PP.
The “means for supporting and dispersing a part of the counterweight W in the range“ (A) ”” shown in FIG. 89 is as if the wheel BB was in contact with the door frame W in FIG. 34, means in which the spring force is dispersed and a part of the spring force becomes a force in the rotational direction, like the force with which the sliding surface presses the wheel in FIG. It is not a “means that a new force that reduces the spring force is added and the rotating body does not rotate unless the force exceeds the resistance”, like the resistance of the door closer.

When the closed door is opened from the state shown in FIG. 89 (c), the sliding surface K extends along the wheel B as shown in FIG. 89 (b). Does not move greatly. In the process of opening the door, the sliding body KK rotates around the wheel B as indicated by D30 indicated by a broken line in FIG. Therefore, the position of the door opening Θd5 when the link A rotates about the connecting shaft C without almost moving the position of the connecting shaft C just before the closing shown in FIG. 89 (b) is the process of opening the door. In FIG. 2, the distance between the “contact point b between the wheel B and the sliding surface K” and the connecting shaft PP is small, and the sealing force is strong.
When the closed canopy is pulled down, it is in a state where it is strongly urged in the closing direction in a range where the opening of the canopy is small, and it is closed again when the hand is released. It will not be in a state of hanging at a stretch.
Even when used on a door whose rotation axis is vertical, the range of deceleration due to insufficient force in the closing process is the range that closes with a strong force in the opening process, and stops wherever you release your hand in the opening process. I will not stay.
When used for a door whose rotation axis is vertical, FIG. 89 is a plan view in which the pivot axis O of the canopy D, the rotation axis Ib of the wheel B, the connection axis C, and the connection axis PP are vertical. The axis of the rotation shaft Sw of the fixed pulley Bc is horizontal, and the suspension body W moves in a direction perpendicular to the paper surface.

FIG. 90 explains a means that two different forces act on the “rotating means in the range (A)” and the “rotating means in the range (A)”. FIGS. 90 (a) and 90 (b) FIG. 90C illustrates a means for switching the “distance between the force action line and the center of rotation”.
In FIG. 90, the urging means Sc is connected between the moving body D that moves along the track R provided in the fixed portion W, the support shaft Ib provided in the mobile body D, and the fixed support shaft Sw provided in the fixed portion. It is an elevation view explaining the operation of the switchgear. The biasing means is an expansion / contraction joint, one side of the cord Sc is attached to the support shaft Ib and the other is attached to the fixed support shaft Sw. Move horizontally. The up and down movement of the counterweight W can be replaced by a spring such as a spring that does not change the spring force even if it is greatly expanded and contracted.
FIG. 90 (a) shows a state in which the moving body D moves horizontally in the direction indicated by the arrow B in the figure when the counterweight W1 falls in the direction indicated by the arrow B in the lower figure. It shows the state of getting over and dropping from the horizontal movement to the point direction.

When one of the counterweights W1 falls, the force pulling the moving body D is weak when the moving body D moves, and as shown in FIG. 90 (b), two counterweights W1 and W2 fall, When moving the moving body D, the force to pull the moving body D is strong. The former is "rotating means in the range (A)" and the latter is "rotating means in the range (I)".
The link A is rotatably supported around a connection axis C provided on the moving body D, and either one of the links A is prevented from rotating by G1 and G2. The support shaft Ib to which one of the cords Sc is attached swings between a position far from the fixed support shaft Sw where the link A comes into contact with G1 and a position where the link A comes into contact with G2 and is close to the fixed support shaft Sw. .

In a state where the link A comes into contact with the contact G1 and the support shaft Ib is fixed at a position far from the fixed support shaft Sw, as shown in FIG. 90 (a), “the gap between the moving body D and the door stop Gd” As the moving body D moves a distance of “δ1”, the second counterweight W2 gets over the pulley BB and falls.
As shown in FIG. 90 (b), the wheel B attached to the rotating shaft Ib of the wheel provided at the tip of the link A moves along the sliding surface K1, and the string Sc crosses the ground of the connecting shaft C. In a state where the link A rotates and moves away from the contact G2 and the support shaft Ib moves to a position far from the fixed support shaft Sw, as shown in FIG. 90 (b), “the gap between the moving body D and the door stop Gd” As the moving body D moves a distance of “δ2”, the second counterweight W2 gets over the pulley BB and falls.
That is, when the opening / closing device has a “switching means” that operates greatly, the moving body D is switched from “a rotating means in the range (A)” to “a rotating means in the range (I)” with little movement.
When the moving body D is moved in a direction opposite to the arrow B in the figure from the state where it is in contact with the door stop Gd and closed, the wheel B moves along the sliding surface K2 and returns to the state shown in FIG. 90 (a).

FIG. 90 (c) uses the rotating mechanism described in FIG. 13 as an urging means instead of the means that uses the vertical movement of the counterweight shown in FIGS. 90 (a) and 90 (b) as a power. J is urged by a spring (not shown) so as to rotate in the direction of arrow A in the figure around the fixed support shaft Sw. The door D moves linearly along the rail R fixed to the door frame W, and the position of the connecting shaft C provided by the door moves from the position when C1 is fully opened toward the position when C6 is closed.
The connecting shaft P and the connecting shaft C at the tip of the rotating body J are connected by two links A and AA, and the two links A and AA are connected by a connecting shaft PP. When the position of the connecting shaft C is from the position of C1 to the position of C5, the two links A and AA are in a straight line, and the "circular motion about the fixed support shaft Sw as the center of revolution" of the connecting shaft P is performed. Change to linear motion.
When the position of the connecting shaft C is from the position of C5 to the position of C6, the contact G and the link A engage with each other so that the rotating body J and the link A rotate relatively integrally. The “circular motion about the fixed support shaft Sw as the center of revolution” of the connecting shaft PP is changed to the linear motion of the connecting shaft C.

The range of the position of the connecting shaft C from the position of C1 to the position of C4 and the position of the connecting shaft P from the position of P1 to the position of P4 is “the connecting shaft P revolving around the fixed support shaft Sw”. Is a range in which the connecting shaft C is pulled, and the links A and AA are kept in a straight line. The “line of action of the force pulling the connecting shaft C”, that is, “the distance between the axis A of the link A and AA and the center of rotation Sw” decreases in proportion to the rotation of the rotating body J, but the distance is large. This is a range in which the rotational force acting around the fixed support shaft Sw is transmitted to a small extent. The movement range of the connecting shaft C and the connecting shaft P is wide, and the rotation angle of the rotating body J is also large.
When the position of the connecting shaft C is in the range from the position of C5 to the position of C6, and the position of the connecting shaft P is in the range from the position of P5 to the position of P6, “the connecting shaft PP revolving around the fixed support shaft Sw” is The range in which the connecting shaft C is pulled and the “distance distance between the axial center line of the link AA and the rotation center Sw” is small, and the moving range of the connecting shaft C is very narrow even if the rotating body J rotates greatly. . The range in which the “switching means” of the “(ki) range” between the “(a) range” and the “(ii) range” operates is such that the movement locus of the connecting axis P is an arc P4P5, Since this approximates the circumference centering on the position C4 of the connecting shaft C just before closing, the connecting shaft C rotates largely without moving and the "magnitude of the force pulling the connecting shaft C""Changes a lot.
From the position of the connecting shaft C to the position of C1 to the position of C5, “the line of action of the force pulling the connecting shaft C”, that is, the distance between the straight link A and the axis of the AA and the center of rotation is Although it decreases in proportion to the rotation of the rotating body J, the connecting shaft C having a large distance has a wide range of movement, and the connecting shaft C has a small distance from the position C5 to the position C6. The moving range is very narrow. In addition, the range in which “switching means” of “(range)” between “(range)” and “(range)” operates is also narrow, and two ranges in which forces of two different magnitudes work That is, it is possible to distinguish between “rotating means in the range of (A)” and “rotating means in the range of (ii)”, and “switching means” exists in the range between them.

FIG. 91 is an explanatory view of the operation of the electric rotating door powered by the electric actuator to the rotating mechanism of FIG. 13 in which the pivot axis O of the door is vertical, and without rotating the tip of the link A, the rotating body J and the link A The crossing angle is adjusted at the position of the contact G provided between the rotating body J and the link A, so that the revolution radius around the fixed support shaft Sw of the connecting shaft PP is freely designed. Similarly to FIG. 90, the width of the “switching means” is adjusted. In the case of FIG. 90, the “switching means” means that the link A and the rotating body J are relatively integrated or released, but even if there is a change in the operation mode of the “switching means”. The movements of the opening process and the closing process are the same except that the directions are reversed. The form is uniquely determined by the opening of the door and the closing process, and there is no difference in form between the opening process and the closing process.

FIG. 91 (a) is a plan view for explaining the operation of “rotating means in the range of (i)” of “range (i) from just before closing to the time of closing”, and FIG. It is an operation explanatory plan view of “rotating means in the range of (A)” of “Area to (A)”.
The rotating body J rotates in the direction of arrow A in the figure around the fixed support shaft Sw fixed to the door frame W, and the door D rotates in the direction of arrow B in the figure about the pivot O of the door. The position of the connecting shaft C moves from the position when C1 is fully opened toward the position when C5 is closed.

The connecting shaft P and the connecting shaft C at the tip of the rotating body J are connected by two links A and AA, and the two links A and AA are connected by a connecting shaft PP. From the position of the connecting shaft C to the position of C1 to the position of C4, the two links A and AA are in a straight line, and the “circular movement about the fixed support shaft Sw as the center of revolution” of the connecting shaft P is connected to the connecting shaft C. Change to linear motion.
When the position of the connecting shaft C is from the position of C4 to the position of C5, G and the link A engage with each other when the rotating body J is attached to the rotating body J, and the rotating body J and the link A rotate relatively integrally. The “circular motion about the fixed support shaft Sw as the center of revolution” of the connecting shaft PP is changed to the linear motion of the connecting shaft C.

The range of the position of the connecting shaft C from the position of C1 to the position of C2 and the position of the connecting shaft P from the position of P1 to the position of P2 is “the line of action of the force pulling the connecting shaft C”, that is, a straight line. The “distance between the axis A of the link A and the AA and the center of rotation Sw” decreases in proportion to the rotation of the rotating body J. The moving range of the connecting shaft P is wide and the rotation angle of the rotating body J is also large. That is, the rotational force acting on the door D is not constant in the “large range from fully open to just before closing” shown in FIG. 91A, but the door rotates with a small rotational force.
When the position of the connecting shaft C is in the range from the position of C4 to the position of C5 and the position of the connecting shaft P is in the range from the position of P4 to the position of P5, “the connecting shaft PP revolving around the fixed support shaft Sw” is The range in which the connecting shaft C is pulled and the “distance distance between the axial center line of the link AA and the rotation center Sw” is small, and the moving range of the connecting shaft C is very narrow even if the rotating body J rotates greatly. .
Although the rotational force acting on the door D is not constant in the “range from just before closing to the closing time (i)”, the door rotates with a large rotational force.

The range in which the “switching means” of the “(ki) range” between the “(a) range” and the “(ii) range” operates is such that the movement locus of the connecting axis P is an arc P3P4. Since this approximates the circumference centered on the position C4 of the connecting shaft C just before closing, the connecting shaft C hardly moves and the rotational force acting on the door D changes from small to large.
3 to 7, the rotational force provided in each range of “(A) range” and “(I) range” is substantially constant, and “(A) range” and “( 90), the rotational force provided in both FIG. 90 and FIG. 91 changes in proportion to the rotation of the rotating body J and changes from “range (A)”. Although the size gradually changes as it moves to “range (ii)”, even if it gradually changes, in the rotation range of the door D, two ranges in which forces of two different magnitudes work, that is, “( There are “rotating means in the range (a)” and “rotating means in the range (ii)”, and “switching means” in the range between them.

As shown in FIG. 91A, in the “switching means”, when the two links A and AA are in a straight line at the moment when the rotating body J and the link A are relatively integrated, the connecting shaft PP Moves parallel to the “closed door surface D0”, and the position of the connecting shaft C temporarily stops. When the connecting shaft P moves from the position of P4 to the position of P5 and the rotating body J rotates greatly, the rotating body J rotates rapidly without adding the door D without rotating, but in this case as well, it is constant. When the electric actuator that rotates at a speed is used as the power, the door is decelerated just before closing and the door is closed after maintaining the stopped state for a long time. In the other embodiments of the present invention, since the “switching means” rotates in the non-addition state as in the case of FIG. 91, it is better to use an electric revolving door than a spring-operated door.

In FIG. 92, “moving body (D) moving along a predetermined trajectory (K)”, a fixing portion (W) provided with the predetermined trajectory (K), and a fixing provided on the fixing portion (W). Opening and closing provided with a support shaft (Sw), a connection shaft (C) provided on the movable body (D), and biasing means (Sc, Bk, W1) between the fixed support shaft Sw and the connection shaft C A device,
The form changes with the operation of the switchgear, and the range in which the moving body D operates due to the change in the form is distinguished into a range where the force acting on the moving body is small (A) and a large range (Yes). And a “switching means” characterized in that the force is continuously changed from small to large or from large to small with or without slight movement of the moving body. A switchgear characterized by that.

In FIG. 92, the moving body is a slider D that moves along the groove K. Patent Documents 9 and 10 are balanced and stationary, and the moving body D does not operate when the form changes. A normal door closer is based on a resistance or other force acting in the opposite direction to the above force, and the magnitude of the force acting on the moving body is not distinguished by changing the form.
In Patent Documents 5 and 6, the force does not change from small to large with slight movement of the moving body. In another embodiment, the moving body is a door D that rotates about the pivot axis O of the door. In FIG. 89, the moving body moves along a rail. In FIG.

In FIG. 93, the urging means is an expansion joint (UV) that changes the distance between the connection shaft (Ib), the fixed support shaft (Sw), and the connection shaft (Ib), and the expansion joint. Operates by the vertical movement of the weight falling due to the deformation of the elastic body or gravity, and the change in the above form is that a new spring force is added to or removed from one spring force, or a new weight is added to one weight. An opening / closing device characterized by adding or removing a weight or moving a force vector.

Other Embodiments In FIG. 93 (a), the expansion joint is a leaf spring UW that bends and deforms. In FIG. 93 (b), the expansion joints are two links A and J. In FIG. 1, the expansion joint is an elastic body that expands and contracts in the axial direction.
FIG. 1 shows a door that is rotated by a spring that is connected to a connecting shaft provided at one end on a door and a fixed supporting shaft provided at the other end on a “door frame or its surrounding wall surface”. Provide one of the support shafts close to the door pivot and the other far away to keep the "distance between the line of action of the spring force and the door pivot or driven shaft" small, and the amount of spring expansion and contraction The door is characterized by its small size. " By reducing the amount of expansion and contraction of the spring, the decrease in the strain energy of the spring can be suppressed to a small extent, and the acceleration of the door can be suppressed to a small level.
67. Switching means in which UV2 is added to the torsion spring UV1 in FIG.
68. Switching means in which V2 is added to the spring V1 in FIG.
Switching means in which weight W2 is added to weight W1 in FIG.
In FIG. 88, the switching means is switching means for separating the weight from the pulley Bc.

FIG. 92 shows a “moving body D that moves along a predetermined track K”, a fixed portion W provided with the predetermined track K, a fixed support shaft Sw provided on the fixed portion W, and a movable body D provided on the moving body D. Description of the operation of the opening / closing device in which a string Sc that pulls the connection shaft C as an urging means is attached between the connection shaft C and the fixed support shaft Sw and the connection shaft C so as to reciprocate. In the plan view, the moving body D is a slider that moves along the groove, a wheel that moves along the sliding surface K, or a sliding door that moves along the rail R in FIG. To do. The urging means is an expansion joint provided between the fixed support shaft Sw and the connection shaft C. The urging means changes the distance between the fixed support shaft Sw and the connection shaft C. It is powered by changes in potential energy due to movement.

In FIG. 92 (a-1 to 3), the piston D reciprocates linearly in the cylinder K, is connected to the counterweight W1 by the string Sc, and the string Sc moves along the pulley Bk. The pulley Bk is mounted on the fixed support shaft Sw, and the fixed support shaft Sw and the cylinder K are fixed to the fixed portion W.
The counterweight W1 falls in the direction of arrow A in the figure by its own weight and is connected by the string Sc, the string Sc moves along the pulley Bk, and the piston D moves in the cylinder K from the start K1 in the direction of arrow B in the figure. Move to end K2.

Fig. 92 (a-1) shows the state where the piston D is at the start end K1 in the cylinder K, Fig. 92 (a-3) shows the state at the end K2, and Fig. 92 (a-2) is in the middle. This shows a state where the counterweight W2 attached to the middle part of the vehicle is about to fall over the pulley Bk.
In the “(A) range” shown in FIG. 92 (a-1), the force pulling the piston D is only the weight of the counterweight W1, and in the (I) range shown in FIG. 92 (a-3). The weight of W2 is added to the weight of counterweight W1.
The movement range of the counterweight changes with the movement of the moving body D, so that the operation range of the moving body D is small (a) and large (yes). It is distinguished by the range. The opening / closing device of FIG. 92 is characterized in that the force is continuously changed from small to large with a slight movement of the moving body D as shown in FIG. 92 (a-2). Switching means ”. When the moving body D is forcibly moved in the direction opposite to the arrow B in the figure, the force continuously changes from large to small.

92 (b-1 to 92) are examples in which the distinction between the range (A) and the range (A) is more prominent, and with a slight movement (movement) of the moving body D, FIG. As shown in (b-2), a “switching means” characterized in that the force is changed from small to large is provided.
In FIG. 92 (b-1 to 3), the wheel B moves along the sliding surface Kw provided on the fixed portion W and the sliding surface Kd provided on the door D simultaneously, and can reciprocate within the sliding surface K. Move linearly. The wheel B and the counterweight W1 are connected by the string Sc, and the string Sc moves along the pulley Bk. The pulley Bk is mounted on the fixed support shaft Sw, and the fixed support shaft Sw and the sliding surface Kw are fixed to the fixed portion W.
As the counterweight W1 falls in the direction of arrow A in the figure, the wheel B moves in the sliding surface Kw from the start end K1 to the end K2 in the direction of arrow D in the figure. At the same time, the wheel B moves in the sliding surface Kd from the start end K3 to the end end K4 in the direction of the arrow C in the figure. As a result, the door D rotates in the direction of arrow B in the figure.

92 (b-1) shows a state where the wheel B is at the start end K1 in the sliding surface Kw, FIG. 92 (b-3) shows a state at the end K2, and FIG. 92 (a-2) is in the middle. This shows a state where the counterweight W2 attached to the middle portion of the string Sc is about to fall over the pulley Bk.
In the “range (A)” shown in FIG. 92 (b-1), the force that pulls the wheel B is only the weight of the counterweight W1, and in the range (ii) shown in FIG. 92 (b-3). The weight of W2 is added to the weight of counterweight W1. “With the moving motion of the moving body D, the load range of the counterweight changes, so that the operating range of the moving body D is larger than the range where the acting force acting on the moving body is small (A). 92, the opening / closing device of Fig. 92 continuously moves from the small to the large with the slight movement of the moving body D as shown in Fig. 92 (b-2). “Switching means” characterized by switching.

The circle Rsw is a circumference centered on the fixed support shaft Sw. Since this is approximate to the circumference of the sliding surface Kw, the counterweight is used while the wheel B moves on the circumference of the sliding surface Kw. There is little movement of W1, and the door D rotates greatly.
The straight portion near the end K2 of the sliding surface Kw is a radial track of the circle Rsw, and the movement of the counterweight W1 is large while the wheel B moves on the straight portion of the sliding surface Kw, and the counterweight W1. The weight of W2 is added to the weight of. The door D rotates small, and the magnitude of the force acting on the door changes from small to large while the door D rotates small.

FIG. 92 uses the change in potential energy due to gravity as power, while FIG. 93 uses the change in strain energy of the elastic body as power.
FIG. 93 shows a “moving body B moving along a predetermined track K”, a fixed portion W provided with the predetermined track K, a fixed support shaft Sw provided on the fixed portion W, and provided on the moving body B. It is an operation explanation elevation view of the opening and closing device that is configured to reciprocate by attaching a leaf spring VW as an urging means between the connecting shaft Ib, the fixed support shaft Sw, and the connecting shaft C, The moving body B is a slider that moves along the groove K and is a wheel B.
FIG. 93 (a-4) is a plan view of the leaf spring VW. As the leaf spring VW approaches the tip, the cross-sectional area becomes smaller and the rigidity becomes smaller. As shown in FIG. 93 (a), the leaf spring VW is designed so that only a short portion near the tip is bent greatly.

93 (a-1) shows a state where the wheel B is at the start end K1 in the cylinder K, FIG. 93 (a-3) shows a state at the end K2, and FIG. Shows the state where UW is going to be in a straight line.
In “range (A)” shown in FIG. 93 (a-1), the leaf spring UW is curved, and the force with which the wheel B presses the sliding surface K is small. In the range (ii) shown in FIG. 93 (a-3), the force acting on the sliding surface K is large because the leaf spring UW is in a straight line. In this way, the range (A) shown in FIG. 93 (a-2) is distinguished from the range (I) shown in FIG. 93 (a-3). The switching device shown in FIG. 92 is characterized in that the force is continuously changed from small to large with a slight movement of the wheel B as shown in FIG. 93 (a-2). Is provided.

FIG. 93 (b-1 to 3) shows a structure in which two links A and J are attached in place of the leaf spring UW of FIG. 93 (a), and “the expansion joint between the fixed support shaft Sw and the connection shaft C” is shown. "Is the two links J and A, and a leaf spring Uv is attached around the connecting shaft P and is urged to rotate. As described with reference to FIG. 63, the “distance between the fixed support shaft Sw and the connection shaft C” increases as it closes. In the range (A) shown in FIG. 93 (b-1), the two links J, A state where A is bent is maintained and the leaf spring Uv shown in FIG. 93 (a) is in a curved state. In the range (ii) shown in FIG. 93 (b-3), the two links J and A are in a state of being close to a straight line, and the leaf spring Uv shown in FIG. 93 (a-3) is in an extended state.

FIG. 94 is an operation explanatory view of the left and right opening / closing bodies Dr and Dl that share the rotation axis O and face each other or approach or separate from each other, and FIGS.
(E) and (f) are examples of the cutting pinch, with the rotation axis O in the middle, the upper half in the figure is the work part, the lower half is the grip part, and FIGS. 94 (a), (c) and (e) are the work parts. (B), (d), and (f) show the opened state.
The work clamp opens the work part in the direction of the arrow B in the figure by closing the grip part in the direction of the arrow B in the figure, and the cutting clip has the work part in the direction of the arrow B in the figure by closing the grip part in the direction of the arrow A in the figure close.

FIG. 94 shows a rotation mechanism having “(a) rotating means”, “switching means”, and “rotating means in the range of (ii)”. At least one of the left and right opening / closing bodies Dr, Dl is rotated. A groove H away from the vicinity of the shaft is provided. The springs Us, Uo for urging the left and right opening / closing bodies Dr, Dl are elastic bodies formed in circular arcs, and at least one of the both ends Sr, Sl is movably attached to one of the opening / closing bodies. If one of the support shafts is a moving support shaft Sr and the other is a fixed support shaft Sl, the moving support shaft Sr swings along the groove H between a “start point K1 close to the rotation axis O” and a distant end point K2. Move.
When the movable support shaft Sr is in a laundry pinch, a strong force acts on the opening / closing body at the end point K2 of the groove with the work portion closed. In the open state, a weak force acts on the opening / closing body at the starting point K1 of the groove. The reverse is true for the cutting pinch.

In FIGS. 94 (a) and 94 (b), both ends Sr and Sl of the spring Us are biased toward each other, and the position of the moving support shaft Sr is the smallest distance Ls between the support shafts Sr and Sl. Stable in position. As shown in FIG. 94 (a), while the laundry basket is closed, the change in the distance Ls is very small while the moving support shaft Sr is shifted from the position of the start point K1 to the position of the end point K2. This means that the transition is slow, and in the closing process from the open state shown in FIG. 94 (b) to the closed state shown in FIG. 94 (a), the moving support shaft Sr stays at the position of the starting point K1 just before the closing, It means that it is transferred almost as soon as it closes. As shown in FIG. 94 (a), if the straight line connecting both ends SR and Sl is Zs, the axial center line of the groove H is Zh, and the crossing angle of the straight lines Zs and Zh is Oz, the crossing angle Oz is as the opening / closing body rotates. The moving support shaft Sr moves to a side that decreases to an acute angle with the intersection angle Oz being a right angle. Assuming that the left and right opening / closing members rotate relatively, the other Dr is fixed and only one Dl rotates, the straight line Zh is fixed, the straight line Zs rotates, and the fixed support shaft Sl moves around the rotation axis O. Revolve.

In FIG. 94 (a), when the straight line Zs when the selection rod is closed is Zs0, the movement support shaft Sr is at the end point K2, and the position S11 when the two straight lines Zh and Zs are orthogonal to each other is the movement support shaft Sr. Is at the starting point K1 and is farther from Zs0 than the position Sl2 when the two straight lines Zh and Zs are orthogonal to each other. This means that the opening degree of the laundry basket is small when the washing basket is opened and the movable spindle Sr starts to move, and the opening degree of the laundry basket is large when the movable spindle Sr starts to move when the laundry basket is closed. This means that as soon as the laundry basket is opened, the spring force becomes weaker and the gripping force becomes stronger during the closing process. FIG. 94 (b) means that once the moving support shaft moves to the position of the starting point K1, the laundry basket is stopped until the moment when it is substantially closed, and the state in which the spring force is weakly applied is maintained except when the laundry basket is closed. ing.

The fact that the moving support shaft Sf easily shifts from the start point K1 to the end point K2 means that it is difficult to return from the end point K2 to the branch K1, and the position of the move support shaft Sf is the end point when closed as shown in FIG. Since the structural form is different between when it is at k2 and when it is at the start point K1 at the time of opening shown in (b), the movement of the apparatus is different between the closing process and the opening process. That is, when you pick up the laundry basket, it will feel as if you have lost your power immediately. Become.

The spring Uo used in FIGS. 94 (c) to 94 (f) is urged in the direction in which both ends Sr and Sl are moved away from each other, and the position of the moving support shaft Sr is the position where the distance Ls between the support shafts Sr and Se is the maximum. It stabilizes at. Further, the moving support shaft Sr moves to the side of increasing to an obtuse angle with the boundary angle Dz being a right angle.
In the embodiment of the cutting pin shown in FIGS. 94 (e) and 94 (f), the moving support shaft S1 moves immediately to the starting point K1 when it is closed from the opened state as shown in FIG. 94 (f), and the action of the spring is reduced. Further, as shown in (e), once it moves to the starting point K1, it continues to stop, and the spring works weakly in a wide range of the opening degree of the pinch. Conversely, in order for the moving support shaft to move immediately from the closed state of (e) so as to exert a restoring force, the crossing angle Θz at the time of closing is close to a right angle as shown in FIGS. Like that. Also, in the case of a laundry nip, in order to prevent it from being released for a while once it is firmly grasped, the intersection angle Θz is set to be away from a right angle as shown in FIGS. 94 (c) and 94 (d) are examples. By changing the direction of the groove in this way, the movement start position of the moving support shaft can be changed.

If the moving support shaft moves from one end to the other end gradually as the opening / closing body opens, instead of suddenly changing from one end to the other end at the predetermined opening of the opening / closing body The strength of the spring gradually changes, the force when working is smaller than the force when not working, and only slightly increases when the force when not working. If it is only necessary to prevent the spring force from increasing so much as it is opened even when the clothes are pinched, it is sufficient to use a spring with low rigidity. However, by providing the “switching means”, even when a spring having high rigidity is used, the force of the spring does not increase so much and the range in which the spring acts can be concentrated at a limited opening. Such a rotation mechanism having a “switching means” is not only an opening / closing body in which both blades rotate relative to the axis of rotation, just like a pinch, but one blade follows a straight groove, such as a press. It can also be applied to a moving body that swings up and down. If the press works only in the downward direction of the blade and the upward direction is due to the restoring force of the spring, and the rotation mechanism shown in FIGS. 94 (c) and 94 (d) is adopted, the force of the spring when the blade moves downward is It weakens and does not reduce the working force of the press, and when the blade moves upward, the force of the spring increases and the spring force lifts the blade upward.

FIG. 95A is an operation explanatory view for explaining the structure of Patent Document 8. One end of the tension spring V is attached to a fixed support shaft Sw at a position different from the rotation axis O of the lid D, and the other end is a support shaft of the wheel B. Attach to Ib. The lid D is provided with a long hole H, and the support shaft Ib of the wheel reciprocates in the long hole H. The lid D only follows the movement of the wheel B by the pulling spring V, and the main operation is as shown in FIG. 95 (b) by the force acting on the wheel supporting shaft Ib. It is an operation that rotates around, and the rotation of the lid D has no meaning in this operation.

In FIG. 95 (a), Rk is a trajectory along which the wheel B moves along the sliding surface K, T is a normal line perpendicular to the sliding surface K, and the sliding surface K is an arc. When passing through the center Ok of the arc. A state when the wheel B moves on the sliding surface K from the start point k1 to the end point k2 is indicated by a solid line in FIG. 95B, and a state at the end k0 is indicated by a broken line.
In FIG. 95 (b), the drawing spring V is not shown. The force action line Fb is on the “axial line Zv of the tension spring V” passing through the wheel support shaft Ib and the fixed support shaft Sw. The force Fb of the tension spring V is decomposed into a force Fk along the sliding surface K and a force Fo orthogonal thereto, the former is a force that moves the wheel B, and the latter is a force that does not move.
Therefore, only Fk of the forces Fk, Fo, Fb revolves the spring V.
FIGS. 95 (a) and 95 (b) show a mechanism for rotating the spring around the fixed support shaft by changing the direction of the spring force Fb, which is rotated by the circumferential force of the circular orbit Rk. The change in the distance Lf between the line of action of the force Fk and the center of rotation Sw of the spring is small.
95 (c) and 95 (d) show the rotation mechanism of FIG. 35. The sliding surface K rotates about the fixed support shaft Sw by the rotational force M, and the link A has a force Fb that the sliding surface K presses the wheel B. To rotate around the rotation axis O.
95 (a) (b) and FIGS. 95 (c) (d) are different in that the member for mounting the wheel B at the tip is a tension spring V or a link A, and is an elastic body. There is a difference between whether or not it exists.
The “distance Lf of the pressing force Fb with respect to the rotation axis O of the action line link A” can be designed to be large at the end of rotation and small until then, and the magnitude of the force acting at the end of rotation, The ratio of the force acting so far can be freely designed to an infinite size. Such a design is not possible with the rotation mechanism of Patent Document 8.

FIG. 96A shows the structure of Patent Document 8, and one end of the spring is attached to a fixed support shaft Sw provided on the door frame W. FIG. When the wheel B is in the middle portion of the sliding surface K, the wheel B and the door D are connected by the link A, so that the wheel B rotates while the wheel B moves, but the spring force Fb is When the wheel B is at the end Ko of the sliding surface K when the wheel B is at the end Ko of the sliding surface K, the door D rotates.
96 (b) and 96 (c), one end of the spring is provided on the door D and becomes an urging force M for rotating the link A. The moment due to the urging force M and the moment due to the pressing force Fb are balanced around the rotation axis Co. As shown in FIG. 96 (c), the door rotates when there is a distance Lf between the line of action of the pressing force Fb and the pivot axis O of the door. FIG. 96 (b) shows the rotation mechanism of Patent Document 6, and when the wheel B is in the middle portion of the sliding surface K, the upper distance Lf is zero and no rotational force acts on the door.

When the wheel B is at the sliding surface end K0 in FIGS. 96B and 96C, the spring force Fb is decomposed into the pressing force Fo and the axial force Fa, and the axial force Fa is increased by the so-called wedge effect.
In FIG. 96 (a), it is possible to increase the axial force Fa by the wedge effect by setting the angle of the link A with respect to the sliding surface Ko in the same manner as in FIGS. 96 (b) and 96 (c). The ratio of the size when Fa is sealed and the size before that can be designed freely. This effect is due to the fact that the line of action of the pressing force Fo and the axial force Fa is arranged in a straight line at a predetermined angle of the door. However, it is not based on the mechanism of Patent Document 8. Nor is it based on a change in the distance L5 between the line of force action and the center of rotation.

FIG. 97 shows that the opening / closing device of FIG. 35 (a) moves the door up and down even with a small force while supporting the heavy weight of the lid so that the door can rotate even with a weak force while the strong spring force is applied. It explains what you can do.
When the lid W is rotated from the horizontal state to the suspended state, the force to rotate from the horizontal state is large, and the force to rotate from the suspended state is small. When rotating from a horizontal state to a suspended state with a constant force, the maximum value of the required force is the smallest. The opening / closing device shown in FIG. 97 (a) makes the force required to open and close the lid as uniform as possible at any position where the lid W moves from the horizontal state to the suspended state so that the lid can be felt lightly when the lid is raised or lowered. It is.
35 (a) has the same structure and operation as those of the opening / closing apparatus of FIG. 35 (a), and each has a feature that the “wheel B moving along the sliding surface K” always climbs a slope with a constant slope, By providing a uniform state throughout the entire process of opening and closing the lid, the lid W can be stationary at any position from the horizontal state to the suspended state, and the force required to open and close the lid is reduced.

FIG. 97 (a) is a drawing explanatory view of the sliding surface KA of the apparatus having the same structure as FIG. 35 (a), and FIG. 97 (b) is an operation explanatory view. FIG. 97 (a) is a drawing explanatory view of the sliding surface KA that continues to supply a constant rotational force to the cam wheel rotating body Jq. The cam is moved along the sliding surface KA with the sliding surface KA fixed and fixed. It is also described that when the wheel B moves, the fixed portion W rotates around the cam body rotation axis Qk.
97 (a) and 35 (a) includes a fixed portion W, a cam wheel rotating body Jq, and a cam body KK, and a wheel B attached to the cam wheel rotating body is provided with a slide provided on the cam body KK. 35 is a link device that moves along the moving surface KA. In FIG. 35, as shown in FIG. 35 (b), the cam wheel rotation body Qj and the cam body rotation axis Qk are fixed to the fixed portion W, respectively. The cam wheel rotating body Jq and the cam body KK rotate about the axis. If it is assumed that the sliding surface KA is fixed and the cam wheel B moves along the sliding surface KA, the fixed portion rotates around the cam body rotation axis Qk as shown in FIG. 97 (b).
The operation of the fixed part shown in FIG. 97 (b) rotating around the cam body rotation axis Qk is such that the axis of the cam body rotation axis Qk is horizontal and the fixed part W is rotated about the cam body rotation axis Qk. FIG. 97 (b) is an elevation view for explaining the operation of the lid.
The lid W rotates from a horizontal state in which the axial center line Zw of the lid W overlaps the X axis to a suspended state in which the axial core line Zw of the lid W overlaps the Y axis. A state where the lid W is horizontal is indicated by a solid line.

The relationship between FIG. 97, FIG. 35, and FIG. 6 will be described.
97, a case where the virtual circle Ra is smaller than the case of FIG. 35 will be described, and a case where the revolution trajectory Rb of the cam wheel B is small will be described in FIG.
In FIG. 97, the virtual circle Ra is smaller and the revolution trajectory Rb of the cam wheel B is larger than in the case of FIG. As a result, the drawn sliding surface KA is more approximate to the circle Rb.
When the virtual circle Ra becomes smaller and the sliding surface KA becomes a circle Rb, when the lid W is in a horizontal state indicated by a solid line, the cam wheel rotating body Jq rotates with the lid stationary, and the cam wheel B is on the sliding surface KA. When the cam wheel B is in the vicinity of the cam body rotation axis Qk on the sliding surface KA, the lid W is in the horizontal state from the suspended state while the cam wheel B is stopped near the cam body rotation axis Qk. Rotate to.
This operation is the same as that described with reference to FIG. 6, that is, the wheel B stays in the vicinity of the pivot axis O of the door, the door rotates from the fully open position to the close position, and the wheel B does not rotate before the close position. This is the same as the operation of moving to a position away from the vicinity of O.

Further, when the sliding surface KA is a circle, the force Fb at which the wheel presses the sliding surface matches the axis of the link A, and a strong axial force acts on the link A. In FIG. 97, when the lid W is in a horizontal state, the lid W remains in a horizontal state regardless of the position of the cam wheel B on the sliding surface KA. The pressing force Fb coincides with the axial center line of the cam wheel rotating body Jq, and the cam wheel rotating body Jq supports the weight of the lid. At this time, the cam wheel B moves on the sliding surface KA even if the rotational force acting around the rotation axis of the cam wheel rotating body Jq is zero.
When the sliding surface KA moves away from the circle Rb, the rotation of the lid is accompanied when the cam wheel B moves on the sliding surface KA. When the lid is nearly horizontal, the cam wheel rotor Jq can rotate the lid with a small rotational force acting around the cam wheel rotor rotating shaft Qj while supporting the weight of the lid. The sliding surface KA in FIG. 6 is a circle, and the wheel B does not move without the rotation of the door. 97 and 35 is separated from the circle Rb, and when the wheel B moves, the door or the lid is rotated.

As the sliding surface KA moves away from the circle Rb, the rotation of the door or the cover increases with the movement of the wheel B. However, the sliding surface KA in FIGS. 97 and 35 has a smaller curvature as it approaches the cam body rotation axis Qk. Therefore, as the wheel B approaches the cam body rotation axis Qk, the “ratio of rotation of the door or lid with respect to the movement of the wheel B” increases.
As shown in FIG. 97 (b), the “rotational force acting around the cam wheel rotating body rotation axis Qj” necessary for moving the lid up and down is large at the beginning when the lid starts to rotate from the horizontal state. Since B moves at a position far from the cam body rotation axis Qk and moves along the sliding surface KA having a large curvature, the wheel B moves greatly and the lid rotates small. The lid can be moved up and down even if the "rotating force" is small.
Further, as the lid shifts to the suspended state, the wheel B moves closer to the cam body rotation axis Qk and moves along the sliding surface KA having a small curvature, and the wheel B moves small and the lid rotates greatly. The “rotational force acting around the rotating shaft Qj of the cam wheel rotating body” required for the increase is large, but it is not necessary to support the weight of the lid for opening and closing the lid as the lid shifts from the horizontal state to the suspended state.

Next, the operation in which the cam body KK rotates around the cam body rotation axis Qk in FIG. 35B and the operation in which the fixed portion rotates around the cam body rotation axis Qk in FIG. 97B are the same. Will be described.
The cam wheel rotator Jq is provided with a wheel rotation axis Ib, the cam wheel B is mounted on the wheel rotation axis Ib, and the cam wheel B revolves around the cam wheel rotator rotation axis Qj in the direction of arrow B However, the sliding surface KA rotates about the cam body rotation axis Qk in the direction of arrow A in the figure and keeps contact with the cam wheel B. Therefore, in FIG. 97 (a), “the sliding surface K and the cam wheel B The contact b ”moves on the“ circle Rb centered on the cam wheel rotating body rotation axis Qj ”. The contacts b0, b1, b2,.
T0, T1, T2,... Are straight lines passing through the contacts b0, b1, b2,... And the wheel rotation axis Ib, and are lines of action of the force with which the sliding surface K presses the cam wheel B. Yes, the cam wheel rotating body rotation axis Qj is kept at a certain distance. The circle Ra is a virtual circle centered on the cam wheel rotating body rotation axis Qj, and the straight lines T0, T1, T2,... Are in contact with the virtual circle Ra, and a0, a1, a2,. is there.

In FIG. 97 (a), circles R0, R1, Rb2,... Are circles having radii a0b0, a1b1, a2b2,. Is a part of the sliding surface K when at the positions of the contacts b0, b1, b2,. Circles R0, R1, Rb2,... Are elements obtained by finely differentiating the sliding surface KA, and the movement of the contacts b0, b1, b2,... Between the cam wheel B and the sliding surface KA is the contact a0. , A1, a2,... Based on approximating a circular motion whose radii are a0b0, a1b1, a2b2,.
Here, since the circles Ra and Rb are concentric circles, the radii a0b0, a1b1, a2b2,... Have the same length, and the broken lines QjabibiRi are all congruent.
The polygonal line QjaibiRi (i = 0, 1, 2,...) Is rotated around the cam body rotation axis Qk and moved to qjikiKi (i = 0, 1, 2,. R1, Rb2,... Are made continuous with R6 to form one sliding surface K0K1K2K3K4K5R6, that is, a sliding surface KA.

In FIG. 97 (a), B0, B1, B2,... Are cam wheels that move while contacting the sliding surface KA at the contacts k0, k1, k2,. Are the action lines of force passing through the wheel rotation axes Ib0, Ib1, Ib2,..., And the straight lines q0j0, q1j1, q2j2,. Line segments k0q0, k1q1, k2q2,... Shown are cam wheel rotating bodies Jq. That is, the rotation axes q0, q1, q2,.
FIG. 97 (b) is obtained by rotating FIG. 97 (a) 180 degrees around the cam body rotation axis Qk. In FIG. 97 (a), line segments k0q0, kq1, k2q2,. 97 (b) corresponds to the cam wheel rotors Jq0, Jq1, Jq2,.
If it is considered that the sliding surface KA is fixed in FIG. 97 (a) and the cam wheel B moves along that, the fixed portion rotates around the cam body rotation axis Qk as shown in FIG. 97 (b).

Next, a change in the moment around the cam body rotation axis Qk will be described.
In FIG. 35, when the force with which the sliding surface K presses the cam wheel B is constant, the “rotation acting around the rotating shaft Qj of the cam wheel rotating body Qj is located anywhere on the sliding surface K. “Moment Mj” is constant. In addition, as the cam wheel B moves away from the cam body rotation axis Qk along the sliding surface K, the cam body rotates with the action lines T0, T1, T2,. As the distance to the axis Qk increases, the rotational moment Mk acting around the “cam body rotation axis Qk of the other rotation axis of the cam wheel rotation body rotation axis Qj” increases.
For example, in FIG. 34, a guide rail is attached around the cam body rotation axis Qk, and the former rotation moment Mj is determined by the change in the distance between the spring axis and the cam body rotation axis Qk and the amount of expansion and contraction of the spring. I try to balance with Mk.

In FIG. 97 (b), when the lid W rotates about the cam body rotation axis Qk in the direction of arrow B in the figure, the center of gravity of the lid W also moves so as to approach the cam body rotation axis Qk in the horizontal direction. The rotational moment Mk "acting around the axis Qk decreases.
In FIG. 35 and FIG. 97 (b), the force having a constant magnitude moves away from or approaches the cam body rotation axis Qk, whereby the “rotational moment Mk acting around the rotation axis” changes. By changing the direction of the former, the latter moves away from or approaches the cam body rotation axis Qk without changing the direction. Therefore, the method of changing the “rotational moment Mk acting around the rotation axis” differs from the former and the latter. The former change and the latter change follow the rotation of the lid. The former change is complicated, but the latter change is relatively simple.

In FIG. 35, the “rotational moment Mk acting around the cam body rotation axis Qk” which is balanced with the “constant rotational moment Mj acting around the cam wheel rotation body Qj” is changed. In (b), the “rotational moment Mj acting around the cam wheel rotary body rotation axis Qj” is changed in proportion to the “rotational moment Mk acting around the cam body rotational axis Qk” which changes due to the movement of the center of gravity of the lid. In FIG. 34, as shown in FIG. 97 (b), it is balanced by the change in the distance between the axis of the “spring mounted around the cam body rotation axis Qk” and the cam body rotation axis Qk and the amount of expansion and contraction of the spring. Is designed so as to be balanced by the change in the distance between the axis of the "spring mounted around the cam wheel rotating body rotation axis Qj" and the cam body rotating axis Qk and the amount of expansion and contraction of the spring.

Next, the balance of moments around the cam body rotation axis Qk will be described.
In FIG. 97, the change in the distance Lw between the line of action of the vertical force w acting on the “connection axis q of the cam wheel rotating body Jq and the lid W” and the cam body rotating axis Qk will be described. The vertical direction acting on the connecting shaft qi (i = 0, 1, 2,...) Between the cam wheel rotating body Jq and the lid W wherever the center of gravity of the lid W is located through the rotation of the lid from the suspended position to the suspended state. The force w i (i = 0, 1, 2,...) Is constant. The distance Lwi (i = 0, 1, 2,...) Between the force wi in the vertical direction and the cam body rotation axis Qk also decreases as the lid W rotates in the direction of arrow B in the figure.
The change in the distance Lf between the action line F of the “force Fb that the sliding surface presses the wheel” following the movement of the cam wheel B and the cam body rotation axis Qk will be described. Virtual circle Ra i (i = 0, 1 , 2,... Moves with the movement on the sliding surface KA of the cam wheel B around the connection axis qi, and rotates with the force action line Ti (i = 0, 1, 2,...). The distance Lfi (i = 0, 1, 2,...) Between the center W and the center Qk also decreases as the lid W rotates in the direction of arrow B in the figure.

The distance Lw between the “action line of the vertical force w acting on the connecting shaft q” and the cam body rotation axis Qk, “the action line of the force Fb that the sliding surface presses the wheel” and the cam body rotation shaft If the distance Lf to Qk is always the same, if the magnitude of the force Fb that the sliding surface presses the wheel is the same as the magnitude of the vertical force w acting on the connecting shaft q, the cam body Although the moments around the rotation axis Qk are balanced, the line between the acting line of the vertical force w acting on the “connection axis q between the cam wheel rotation body Jq and the lid W” and the cam body rotation axis Qk. The change in the distance Lw is different from the change in the distance Lf between the action line F of the “force Fb that the sliding surface presses the wheel” and the cam body rotation axis Qk according to the movement of the cam wheel B.
The difference between the former distance Lw and the latter distance Lf is made to balance the moment around the cam body rotation axis Qk by changing the magnitude of the force Fb with which the wheel presses the sliding surface.

At the beginning of the rotation of the lid W from the horizontal state, both the distance Lwi and the distance Lfi change little, and both the distance Lwi and the distance Lfi change greatly as the lid W approaches the suspended state. However, the change in the distance Lfi with respect to the change in the distance Lwi increases as the lid W approaches the suspended state from the beginning of rotating from the horizontal state, and the moment due to the force wi around the cam body rotation axis Qk is the pressing force Fb. It becomes larger than the moment by.
In the lid opening / closing mechanism shown in FIG. 97, the intersection angle Θj with the axis Zj of the cam wheel rotating body Jq is constant throughout the entire process of rotating the lid from the horizontal state to the suspended state, and the wheel presses the sliding surface. Since the magnitude of the force Fb to be rotated is proportional to the rotational moment Mk acting around the cam body rotation axis Qk, the wheel W is increased by increasing the rotational moment Mk as the lid W approaches the suspended state from the beginning of rotating from the horizontal state. The force Fb for pressing the sliding surface is increased so as to balance the moment due to the force wi around the cam body rotation axis Qk.
As shown in FIG. 97 (b), a tension spring V is attached around the cam body rotation axis Qk, and the cam wheel rotation body Jq is urged to rotate in the direction opposite to the arrow a in the figure, and the lid W is shown in the figure. When the cover W is rotated in the direction opposite to the arrow B, the force of the pulling spring V that approaches the suspended state from the beginning when the lid W starts to rotate from the horizontal state increases, and the moment due to the force wi around the cam body rotation axis Qk It can be adjusted so that the moment by the pressing force Fb is balanced.

The sliding surface KA shown in FIG. 97 is originally a sliding surface KA that rotates the door with a constant rotational force as shown in FIG. 35, and the sliding surface KA shown in FIG. 97, the sliding surface KA shown in FIG. 97 is easy even though the cam wheel B supports the large weight of the lid. To be moved to. In addition, the rotating mechanism shown in FIG. 97 is to downsize a device that easily swings a heavy lid up and down.
97. When the lid shown in FIG. 97 is used to grasp or crush or cut an object while grasping it, it is required that the lid rotational force increases as the lid rotates without causing a large weight of the lid. In this case, the cam wheel B moves on the sliding surface KA not by a spring but by an electric actuator.

The case where the virtual circle is large in FIG. 98 and the revolution trajectory Rb of the cam wheel B is small will be described.
As shown in FIGS. 15 and 16, the sliding surface KA is a circle Rb so that a strong axial force acts on the link A when the “force Fb that the wheel presses the sliding surface” and the axial center line of the link A coincide with each other when sealed. In this case, the force Fb that presses the sliding surface and the axial center line of the cam wheel rotating body Jq coincide with each other regardless of the position of the wheel, and the cam wheel rotating body Jq supports the weight of the lid. Moreover, since the lid does not rotate even when the cam wheel rotating body Jq rotates, no force is required to move the cam wheel.
On the other hand, when the virtual circle is large and the revolution orbit Rb of the cam wheel B is small as shown in FIG. 98, the sliding surface KA is greatly separated from the circle Rb, and “the tangential direction of the revolution of the cam wheel B and the cam wheel rotation The crossing angle Θj of the body Jq with the axis Zj of the body Jq increases, the cam wheel B moves a little and the lid W rotates greatly, and the force that the cam wheel rotor Jq supports the dead weight of the lid W decreases. A large force is required to rotate the.
When the “intersection angle Θj between the revolution tangent direction of the cam wheel B and the axial center line Zj of the cam wheel rotating body Jq” exceeds a right angle as in the “switching means” shown in FIGS. In order for the cam wheel rotating body Jq to support the weight of the lid so as to move greatly when a pressing force is applied, a large force is required to prevent the cam wheel from moving. In order for the wheel B to revolve and the lid W to move up and down, a large rotational force needs to work around the “rotating axis q of the cam wheel rotating body Jq”.

In both FIG. 97 and FIG. 98, throughout the entire process of rotating the lid W from the horizontal state to the suspended state, the “intersection angle Θj between the tangential direction of revolution of the cam wheel B and the axis Zj of the cam wheel rotor Jq” is It is constant. This indicates that the ratio of “the force Fb that the cam wheel B presses the sliding surface KA” and “the component force Fr in the tangential direction of the revolution of the cam wheel B” is constant, as indicated by the arrow Fb6 in the figure. Meaning, “the component force Fr in the tangential direction of the revolution of the cam wheel B” means the rotational force in the direction of the arrow “a” in the figure acting around the “rotating axis q of the cam wheel rotating body Jq”.
Throughout the entire process from the horizontal state to the state where the lid W is suspended, the distance between the line of gravity acting on the center of gravity of the lid and the cam body rotation axis Qk, and the “action of the force that the cam wheel B presses the sliding surface KA” When the distance between the line Fb "and the cam body rotation axis Qk is equal, it works around" the tangential component force Fr of the revolution of the cam wheel B ", that is," the rotation axis q of the cam wheel rotation body Jq ". If the rotational force is constant, the “moment about the cam body rotation axis Qk” is balanced.

Considering the case where the cam wheel B moves along the sliding surface KA and the case where the cam wheel B moves along the “circumference Rc centered on the fixed point C”, the lid W is in a horizontal state in both the former case and the latter case. The gravity action line acting on the center of gravity of the lid and the "action line Fb of the force by which the cam wheel B presses the sliding surface KA" both approach the cam body rotation axis Qk as it rotates to the suspended state. In this case, the “intersection angle Θj between the tangential direction of revolution of the cam wheel B and the axis Zj of the cam wheel rotating body Jq” is constant, and is not constant in the latter case. In the latter case, as shown by the intersection angle Θc1 in the figure, the intersection angle Θj increases as the cam wheel B approaches the cam body rotation axis Qk, and the “component force Fr in the tangential direction of the revolution of the cam wheel B” increases. If the rotational force acting around the “rotating axis q of the cam wheel rotating body Jq” is not large, the “moment about the cam body rotating axis Qk” will not be balanced.
In this way, through the entire process from the horizontal state to the state where the lid W is suspended, the intersection angle Θj is constant, the distance between the line of gravity acting on the center of gravity of the lid and the cam body rotation axis Qk and the “cam When the distance between the action line Fb of the force with which the wheel B presses the sliding surface KA and the cam body rotation axis Qk are equal, the “moment about the cam body rotation axis Qk” is balanced.

When the virtual circle is large with respect to the revolution track Rb of the cam wheel B as shown in FIG. 98, the change in the curvature of the sliding surface KA is larger than that in FIG. In the case of FIG. 98 when the lid W is in a horizontal state, the lid does not remain stationary even when the cam wheel rotator Jq rotates, as compared to the case of FIG. 97. , The cam wheel rotor Jq has little force to support the weight of the lid W. At the same time, a large force is required to rotate the lid W.
However, when the virtual circle is large with respect to the revolution trajectory Rb of the cam wheel B, the length of the cam wheel rotating body Jq is shorter than that in FIG. 97, and the moving range of the wheel is a position away from the cam body rotating axis Qk. In the range where the lid W is slightly rotated from the horizontal state, the “distance Lf between the force action line Fb and the rotation center Qk” is kept long. Compared to FIG. 97, “the distance between the gravity action line acting on the center of gravity of the lid and the cam body rotation axis Qk”, “the action line Fb of the force with which the cam wheel B presses the sliding surface KA, and the cam body rotation axis. "Distance between Qk" is more equal.

The door opening / closing apparatus shown in FIG. 35 has a rotating shaft that is vertical and maintains a balance with the rotational resistance around the pivot axis O of the door, thereby minimizing the force required to open and close the door. The lid opening / closing device of FIGS. 97 and 98 has a horizontal rotation axis, and keeps a balance with the rotational moment around the lid rotation axis accompanying the movement of the center of gravity of the lid, thereby minimizing the force required to open and close the lid. To do. In any case, the intermediate portion of the sliding surface KA is designed to maintain a balanced state. In addition, a small rotational force acts on the rotating shaft of the cam wheel rotating body Jq to rotate.
The intermediate portion of the sliding surface KA shown in FIG. 35 is a portion that engages “rotating means in the range (A)”, and the cam wheel rotating body Jq retains a large axial force so that it does not act on the door. The middle part of the sliding surface KA shown in FIGS. 97 and 98 is a part that carries “rotating means in the range (ii)”, and the cam wheel rotating body Jq supports a large axial force and acts on the lid. A large axial force works effectively in the same manner as the sealing mechanism shown in FIGS. “Rotating means in range (ii)” is the last range of rotation in FIGS. 15 and 16, but is the entire range of rotation in FIGS. 97 and 98.

The end of the sliding surface KA shown in FIG. 35 greatly changes the curvature of the sliding surface KA so that a large sealing force acts in the case of a door. In the case of the lid in FIG. 98, the lid is fixed. In this way, steps KA0 and KA6 are provided at both ends of the sliding surface KA to provide a locking portion that prevents the reverse rotation of the lid. The “distance Lf between the force action line Fb and the rotation center Qk” is small at both ends of the sliding surface KA in FIG. The force is acting in the direction to do.
If the force for feeding the lid to the engaging portion is added at both ends of the sliding surface KA in FIG. 98, the balance between the rotational moment due to the weight of the lid and the moment against it is not a problem.

FIG. 99 (a) is a drawing obtained by rotating FIG. 36 (b) by 180 degrees. In FIG. 36, the cam wheel B moves along the outside of the sliding surface K, whereas in FIG. It moves along the inside of the sliding surface K.
In FIG. 99, as in FIG. 36, the fixed portion W is provided with a pair of rotating shafts, that is, a cam wheel rotating body rotating shaft Qj and a cam body rotating shaft Qk, and the cam wheel rotating body Jq and cam body KK are respectively used as axes. And rotate. The cam wheel rotating body Jq and the cam body KK are provided with a wheel rotating shaft Ib and a sliding surface K, respectively, and the cam wheel B is mounted on the wheel rotating shaft Ib, and the cam body KK rotates the cam wheel rotating body. By rotating in the direction of arrow A in the figure around the axis Qj, the sliding surface K presses the cam wheel B, and the cam wheel B revolves in the direction of arrow B in the figure about the cam wheel rotating body rotation axis Qj. To do. FIG. 99A is a drawing explanatory view of the sliding surface K that provides a constant rotational force to the cam wheel rotating body Jq, and FIG. 99B is an operation explanatory view.
The cam wheel rotating body Jq and the cam body KK are not shown in FIGS. 99 (a) and 36 (b), but are shown in FIG. 99 (b).

A circle Rb is a circle centered on the rotating shaft Qj of the cam wheel rotating body and is a locus of the contact b between the sliding surface K and the cam wheel B, and the contacts b0, b1, b2,. The position moved from moment to moment is shown.
In FIG. 99A, T0, T1, T2,... Are straight lines passing through the contacts b0, b1, b2,... And the wheel rotation axis Ib, and the sliding surface K presses the cam wheel B. This is a line of action of the force to be maintained and is kept at a constant distance from the cam wheel rotating body rotation axis Qj. A circle Ra is a circle centered on the rotating shaft Qj of the cam wheel rotating body, and is a common virtual circle in contact with the straight lines T0, T1, T2,.

Here, when the force with which the sliding surface K presses the cam wheel B is constant, the “rotational moment Mj acting around the rotating shaft Qj of the cam wheel rotating body” is constant, and the cam wheel B acts on the sliding surface K. As the distance from the cam body rotation axis Qk increases, the distance between the straight lines T0, T1, T2,... And the cam body rotation axis Qk increases and the “rotational moment Mk acting around the cam body rotation axis Qk” increases. To do. That is, the “rotation moment Mk acting around the cam rotation axis Qk” that increases as the cam wheel B moves away from the cam rotation axis Qk along the sliding surface K is always constant. It is balanced with the “rotating moment Mj that works around”.

99A, circles R0, R1, Rb2,... Are circles having radii a0b0, a1b1, a2b2,... Centered on the contacts a0, a1, a2,. Is a part of the sliding surface K when at the positions of the contacts b0, b1, b2,. Here, since the circles Ra and Rb are concentric circles, the radii a0b0, a1b1, a2b2,... Have the same length, and the broken lines QjabibiRi are all congruent.
When the polygonal line QjabiBiRi (i = 0, 1, 2,...) Is rotated around the cam body rotation axis Qk and moved to qijkiKi (i = 0, 1, 2,...), The circles R0, R1. , Rb2,... Form one sliding surface K0K1K2K3K4K5 continuous with R5. Further, q0, q1, q2,... Qj move on a circle Rq centering on the cam body rotation axis Qk.

In FIG. 99 (a), the cam wheel rotating body Qj and the cam body rotating shaft Qk are fixed to the fixed portion W, and the cam wheel rotating body Jq and the cam body KK rotate about the respective shafts. Assuming that K0K1K2K3K4K5 is fixed and the cam wheel B moves along the K0K1K2K3K4K5, the fixed portion rotates around the cam body rotation axis Qk as shown in FIG.
In FIG. 99 (a), B0, B1, B2,... Are cam wheels that move while contacting the sliding surfaces K0K1K2K3K4K5 at the contacts k0, k1, k2,. It corresponds to cam wheels B0, B1, B2,.
In FIG. 99 (a), straight lines k0j0, k1j1, k2j2,... Are lines of action of forces passing through the wheel rotation axes Ib0, Ib1, Ib2,..., And straight lines q0j0, q1j1, q2j2,. Lines Ib0q0, Ib1q1, Ib2q2,... That are not shown are distances between the force action line and the center of revolution of the cam wheel B, and the cam wheel rotors Jq0, Jq1, Jq2,. It corresponds to.

FIG. 99 (a) shows a state in which the cam wheel rotating body rotation axis Qj is fixed to the fixed portion W, the sliding surface K presses the cam wheel B, and the cam body KK rotates around the cam body rotation axis Qk. When the cam wheel B presses the sliding surface K in a state where the sliding surface K is fixed to the fixed portion W, the fixed portion W is camped as shown in FIG. 99 (b). The cam wheel rotation body rotation axis Qj rotates about the body rotation axis Qk.
Next, the fixed portion W shown in FIG. 99 (b) is considered to be a lid that rotates up and down around the cam body rotation axis Qk, and the cam wheel rotation body Jq is illustrated with the connection axis q provided on the lid W as an axis. The cam wheel B that rotates in the direction of the middle arrow A and moves on the cam wheel rotating body Jq moves along the sliding surface K fixed to the fixed portion W in the direction of the arrow C in the figure, and the lid W moves to the cam body rotating shaft Qk. Suppose that the axis rotates in the direction of the arrow B in the figure.
Here, the cam core rotating shaft Qk and the connecting shaft q have a horizontal axis, and FIG. 99 (b) shows a swing between the lying state indicated by the solid line and the standing state indicated by the one-point difference line W0. It is an elevation view explaining the operation | movement which moves.

G0, G1, G2,... On the alternate long and short dash lines W0, W1, W2,. When the lid W rotates about the cam body rotation axis Qk in the direction of the arrow B in the figure, the center of gravity also moves in the horizontal direction. The “rotational moment Mk acting around the cam body rotation axis Qk” decreases as the cam wheel B approaches the cam body rotation axis Qk along the sliding surface K.
The sliding surface KA shown in FIG. 99 is substantially straight, and the force action lines k0j0, k1j1, k2j2,... Shown in FIG. 99 (a) are substantially parallel, and the force action lines k0j0, k1j1, k2j2. ,... And the cam body rotation axis Qk, and the corresponding distance between the “vertical load acting on the connection axis q” and the cam body rotation axis Qk. Further, as explained in FIG. 99 (a), “rotational moment Mj acting around cam wheel rotation axis Qj” that balances “rotation moment Mk acting around cam rotation axis Qk” is always constant. The lid W can be rotated from the lying down state to the standing state by continuing a constant rotational force around the cam wheel rotating body rotation axis Qj.

Since the gradient of the sliding surface K is always constant with respect to the moving direction of the wheel B at the contact point between the wheel B and the sliding surface K, the cam wheel B is located at any position on the sliding surface K. It moves along the sliding surface K by a constant rotational force. Further, since the intersection angle Θj between the “force Fb at which the wheel presses the sliding surface” and the axial center line of the cam wheel rotating body Jq is small, the cam wheel B supports the cam force with a small force Fm. B moves along the sliding surface K.

FIG. 100 is an elevational view for explaining the operation in which the opening / closing body W rotates in the direction indicated by the arrow B in FIG. 100 (a), (b), and (c), the shape of the cam body sliding surface K that rotates about the rotation shaft Q provided on the opening / closing body W is the involute curve described in FIG. The cam body rotation shaft Qk is provided on the opening / closing body W, and the cam body KK is mounted on the cam body rotation shaft Qk. When the cam body KK rotates in the direction of arrow A in the figure while being in contact with the carriage KAA, the carriage KAA moves in the direction of arrow C in the figure, and the opening / closing body W rotates in the direction of arrow B in the figure. Wheels BB are mounted on both ends of the carriage KAA, and the wheels BB move along the surface H.
100 (a), (b), and (c) show a state in which the opening / closing body W is lying down, a state in the middle of rotation, and a state in which it stands.

When the shape of the cam body sliding surface K of the cam body KK is an involute curve as described with reference to FIG. 80, the plane KAA moves in parallel when the cam body KK rotates along the plane KAA, but FIG. The operation when the cam body KK moves while rotating with the KAA fixed is described.
As described with reference to FIG. 80, also in FIG. 100, when a constant rotational force M continues to act around the cam body rotation axis Qk, a constant pressing force Fb continues to act on the plane KAA. The pressing force Fb works perpendicularly to the plane KAA.
Throughout the entire process of rotating the opening / closing body W, the intersection angle between the action line Z of the weight acting on the cam body rotation axis Qk and the working ship of the pressing force Fb is constant at the end, and the above-mentioned intersection angle when the plane KAA is horizontal. Becomes a right angle. If the crossing angle is not right but constant, the change in the distance Lf between the line of action of the pressing force Fb and the rotation axis Q is the same whether the crossing angle is right or not. In the balance of moments around the rotation axis Q, a constant relationship is established between the moment due to the weight acting on the cam body rotation axis Qk and the moment due to the pressing force Fb. Therefore, the upper surface of the carriage KAA may not be a horizontal plane.
When the carriage KAA moves along the horizontal plane H, the plane KAA on which the cam body sliding surface K moves is the horizontal plane H, and the pressing force Fb and the weight acting on the cam body rotating shaft Qk are the same in size. Moreover, the working direction is the same in the vertical direction.
Throughout the entire process of rotating the opening / closing body W, the pressing force Fb supporting the weight acting on the cam body rotating shaft Qk is a constant force, and the direction of the pressing force Fb is constant. This means that the maximum value of force required to do this is the smallest.

A description will be given of the movement of the contact surface KAA in the direction indicated by the arrow C in FIG.
In FIG. 100 (a), the position on the contact surface KAA in contact with the cam body KK is ba0 and the position on the cam body sliding surface K is bb0. When bb0 is on the vertical line Z passing through the cam body rotation axis Qk, if the contact point between the cam body KK and the contact surface KAA is b in FIG. The length of the outer edge portion of K is longer than the “distance r between the gravity action line and the force action line Fb”, and the carriage KAA is shown in FIG. It will move in the direction of the middle arrow c.

As shown in FIG. 100 (b), in a state where the opening / closing body W is close to being overlaid, the cam body rotating shaft Qk rises greatly with respect to the rotation of the cam body KK, and the cam body rotating shaft Qk with respect to the rotation of the opening / closing body W. This is consistent with the large rise. Also, as shown in FIGS. 100 (c) and 100 (d), in the state where the opening / closing body W is almost upright, the cam body rotation axis Qk hardly rises with respect to the rotation of the cam body KK, and the cam This corresponds to a small increase in the body rotation axis Qk. Thus, the rotation speed of the opening / closing body W approximates the rotation speed of the cam body KK and the rotation speed of the opening / closing body W approximates the moving speed of the contact surface KAA until the opening / closing body W changes from the lying down state to the standing state.

When the outer edge portion of the cam body KK is in direct contact with the horizontal plane H without passing through the carriage KAA, slip occurs between the outer edge portion of the cam body KK and the horizontal plane H, and friction occurs, resulting in great resistance to rotation of the cam body KK. 100 (a) to (d), the horizontal plane H moves with the rotation of the cam body KK, so that the outer edge of the cam body KK and the horizontal plane H in FIGS. Are in contact with each other via the wheel B, so that no great resistance is applied to the rotation of the cam body KK.
FIG. 100 (a) is an embodiment in which blades are applied to both the outer edge portion of the cam body sliding surface K and the contact surface KAA so as to be engaged with each other, but FIGS. 100 (b) and 100 (c) are blades. This is an example in which is not applied.
In FIG. 100 (a), the contact surface KAA can be driven in the direction of arrow C in the figure to rotate the cam body KK in the direction of arrow a in the figure.

In FIGS. 97 and 99, the rotational force M is applied around the rotational axis q provided on the opening / closing body W to rotate the cam wheel rotating body Jq. In this case, the cam wheel KK is positioned between the outer edge of the cam body KK and the cam wheel B. Even if sliding occurs, it is sufficient that friction does not occur, and it is not necessary to apply a blade to both the outer edge portion of the cam body sliding surface K and the contact surface KAA so as to be engaged with each other. Similarly, in FIG. 100, when the opening / closing body W is rotated around the cam body rotation axis Qk by rotating the opening / closing body W, a slip occurs between the outer edge of the cam body KK and the horizontal plane H, and no friction occurs. Well, it is not necessary to apply a blade as shown in FIGS.

The cam body KK shown in FIG. 100 (d) is in an inverted relationship with the cam body KK shown in FIGS. 100 (a), (b) and (c), and the cam body KK presses the sliding surface H. In FIG. 100 (d), the force acting line Fb is on the side closer to the cam body rotation axis Qk and on the far side in FIGS. 100 (a) and 100 (b).
When the opening / closing body W shifts from the lying down to the standing state, both the distance Lw between the gravity action line and the rotation axis Q and the distance Lf between the force action line Fb and the rotation axis Q decrease.
In FIG. 100 (d), the distance Lf approaches zero, and no matter how large the force Fb is, the force for rotating the opening / closing body W disappears. As shown in FIG. 100 (d), the opening / closing body W is not rotated at a position where the line of force Fb passes through the rotation axis Q.
Similarly, the distance Lw approaches zero in FIGS. 100A, 100B, and 100C. When the distance Lw approaches zero, gravity does not rotate the opening / closing body W, and there is no force to rotate the opening / closing body W at a position where the gravity action line Z passes through the cam body rotation axis Qk.

Since the “distance r between the gravity action line and the force action line Fb” is constant throughout the entire process of the opening / closing body W transitioning from lying down to standing, considering the balance of moments about the rotation axis Q. The magnitude of the force Fb that balances the rotational moment in the direction opposite to the arrow B in the figure due to gravity approaches infinity in FIG. 100 (d) and approaches infinity in FIGS. 100 (a), (b), and (c). . In a state where the opening / closing body W is nearly upright, the force for rotating the opening / closing body W in the direction of the arrow B in the figure is large in FIG. 100 (d) and small in FIGS. 100 (a), 100 (b), and 100 (c). Considering the balance of moments around the rotation axis Q in a state where the opening / closing body W is close to lying down, “the gravity action line and the rotation axis Q are There is little change in “distance r”, and the ratio of “distance r between gravity action line and rotation axis Q” and “distance r between force action line Fb and rotation axis Q” is substantially constant. Therefore, the opening / closing body W can be rotated and the center of gravity can be raised by continuing to apply a substantially constant applied force around the cam body rotation axis Qk. In most rotations of the opening / closing body W in which the center of gravity rises, the opening / closing devices in FIGS. 100A, 100B, and 100C efficiently convert the rotational force into the rise in the center of gravity.

The movement of the contact surface KAA in the direction of the arrow C in the figure as the cam body KK rotates will be compared.
With the rotation of the cam body KK, the contact surface KAA moves in the direction of being drawn into the cam body rotation axis Qk. In FIGS. The direction drawn in is the direction approaching the rotation axis Q, and the vertical line Z passing through the cam body rotation axis Qk is the same direction as the direction approaching the rotation axis Q, and the movement of the contact surface KAA in the direction indicated by the arrow C in FIG. .
In FIG. 100 (d), the contact surface KAA is drawn in the cam body rotation axis Qk away from the rotation axis Q, and is opposite to the direction in which the vertical line Z passing through the cam body rotation axis Qk approaches the rotation axis Q. The movement of the contact surface KAA in the direction of the arrow C in the figure is offset and becomes smaller.
As shown in FIG. 100 (a), the cam body KK is driven by driving the contact surface KAA in the direction indicated by the arrow C in such a manner that both the outer edge of the cam body KK and the contact surface KAA are engaged and engaged with each other. When rotating in the direction of the middle arrow A, the force for rotating the opening / closing body W in the direction of the arrow B in the figure is large in FIG. 100 (d) and small in FIGS. 100 (a), 100 (b), and 100 (c) convert the rotational force into a rise in the center of gravity efficiently.

In FIGS. 100 (a), (b), and (c), the contact surface KAA in contact with the cam body KK can be moved, so that resistance to rotation of the cam body KK is eliminated. ), Even if a plurality of wheels B are arranged on the outer edge portion of the cam body KK, and even if a plurality of wheels B are arranged on the horizontal plane H as shown in FIG. The rotation of the cam body KK can be transmitted to the opening / closing body W in the state where no is accompanied.

100 (e) and (f) are the ones to which the spiral wheel described in Patent Document 11 is attached in place of the cam body KK of FIGS. 100 (a), (b) and (c), and the spiral wheel is centered. It is formed by successively superposing right triangles whose height is the radius of the virtual circle Ra as a vertex, and the hypotenuse of the previous right triangle becomes the base of the next right triangle. The shape of the right triangle is determined by the radius of the virtual circle Ra, and the shape of the spiral wheel is uniquely determined by the radius of the virtual circle Ra in the same manner as the shape of the cam body KK in FIGS. 100 (a), (b), and (c). decide.
Comparing the shape of the spiral wheel drawn by the same virtual circle with the shape of the cam body KK, in the former case, the differential element of the spiral wheel is a line segment perpendicular to the radial direction, and the arc shown in FIG. Because it is closer to the cam body rotation axis Qk than the differential element Ri. As the former moves away from the rotation axis Qk, the degree of convergence to a circle increases and approximates to a circle more. Further, the amount of increase in the rotation axis Qk accompanying rotation is small.
In this way, the former and the latter are clearly different. If two curved lines are defined by the same virtual circle and one is an involute curve, the other is not an involute curve.

As shown in FIG. 100 (e), when the wheel B is mounted with two vertices other than the right triangle as the axes, and the two wheels B come in contact with the horizontal plane H, the rotational force M acting around the cam body rotation axis Qk. As shown in FIG. 100 (f), when one wheel B contacts the horizontal plane H and the spiral wheel rotates, the distance lf from the vertical line passing through the cam body rotation axis Qk decreases. The rotational force M decreases.
On the other hand, when the cam body KK shown in FIGS. 100A, 100B and 100C rotates while contacting the horizontal plane H, an infinite number of wheels are arranged on the horizontal plane H as shown in FIG. Thus, the friction between the cam body KK and the horizontal plane H is reduced, and the decrease in the rotational force M from the time when the two wheels B contact the ground until the time when the one wheel B contacts the ground is smaller than that in the former case. The rotational force M is more uniform throughout the entire process of rotating the opening / closing body W around the rotation axis Q.

In the case of FIGS. 100A, 100B, and 100C, the contact between the cam body KK and the horizontal plane H is limited to one point, and the rotational force M is more uniform than the former. The fact that the rotational force M is more uniform throughout the entire process of rotating around the rotation axis Q means that the force for rotating the opening / closing body W is the smallest.
FIG. 100 shows the sliding surface K as a horizontal plane so that the length of the cam wheel rotating body Jq in FIGS. 97 to 99 changes continuously as shown in FIGS. 100 (e) and (f). .

Features common to the switchgears of FIGS. 97, 99, and 100 will be described.
As shown in FIG. 100 (a), blades are applied to both the outer edge portion of the cam body sliding surface K and the contact surface KAA to drive the contact surface KAA to rotate the cam body KK to move the opening / closing body W up and down. 97 and 99, blades can be applied to both the cam body sliding surface KA and the cam wheel B to rotate the cam wheel B to rotate the cam body sliding surface KA. These are gear mechanisms in which the pinion moves along the internal gear or the external gear, and the internal gear or the external gear is not a circle but a vortex line, and the rotation transmission mechanism in which the speed ratio continuously changes. Further, unlike the transmission mechanism that transmits the continuous rotation of the gear, the opening / closing mechanism is accompanied by a rotation that swings between a start point and an end point, and the cam wheel sliding surface KA is rotated a number of times by the cam wheel B. It is to convert to.

As shown in FIGS. 69 (a) to 69 (c), an opening / closing device using a reciprocating motion of a piston moving in a cylinder by an opening / closing device that connects a door and a door frame with an expansion joint is shown in FIGS. A biasing means for supporting the weight of 100 opening / closing bodies W with an expansion / contraction joint, in which a force acts in the tangential direction of the circular motion of the opening / closing body W, and for incorporating the rotational motion of the opening / closing body W into the expansion / contraction joint. It moves with. The biasing means needs a force that opposes the weight of the opening / closing body W.
Compared to this, in the opening / closing device of FIGS. 97, 99, and 100, the portion that supports the weight is not a biasing means but a rigid body, and a force acts in the radial direction of the circular motion of the opening / closing body W. Regardless of the weight of the opening / closing body W, the biasing means may be such that the direction of the force for rotating the opening / closing body W is perpendicular to the direction of supporting the weight and the force is small. The switchgears of FIGS. 97, 99, and 100 have a common feature of rotating with a small force while supporting a large weight or resisting a large force.

As described with reference to FIGS. 35 to 37, in the door opening and closing device when the rotation axis is vertical, the shape of the sliding surface K is such that the rotational force acting on the door and the maximum static friction force acting on the door pivot O are balanced. Designed to. When the rotation axis is vertical, the door opening and closing device is designed such that the shape of the sliding surface K is balanced between the rotational force acting on the door and the maximum static friction force acting on the pivot axis O of the door.
97, 99, and 100, the lid opening / closing device in the case where the rotation axis is horizontal has the shape of the sliding surface K so that the rotational force acting on the lid and the rotation of the lid acting around the rotation axis of the lid. It is designed to balance the “rotational moment due to the weight of the lid that changes with the balance”. In both cases, the balance is designed to be balanced, the former is to make the rotational force acting on the door more than the above-mentioned balanced force, and the latter is to make the rotational force acting on the lid equal to the above-mentioned balanced force and keep it stationary. is there.
For the door when the rotation axis is vertical, the balance condition is also satisfied for the lid when the rotation axis is horizontal so that the door rotates when a slight force is applied when the balance condition is satisfied. Rotate by adding a slight force at.

97, 99, 100 is a device that rotates with a small force while supporting a large weight, and is a device that swings up and down around a horizontal rotating shaft like a crane beam or a drawbridge like a lid. It can be used as an actuator. Further, since the slight rotation of the cam body sliding surface KA is converted into multiple rotations of the cam wheel B, the cam wheel B can be opened and closed by multiple rotations of the cam wheel B and the same day of continuous change. It can be used as an actuator for cutting or crushing tools.
Contrary to its use as an actuator, it can be used as a means for generating electric power by converting a slight rotation of the “opening / closing body that swings when a large force acts” into a number of rotations of the cam wheel B. The switchgear of FIGS. 97, 99 and 100 can extract only the rotation effective for power generation while supporting a large weight. For example, a large force acts on the flow of the tide and the fullness of the tide once a day, so that the large opening / closing body can be swung. It is excellent in that it has a structure that supports a large force as a means of changing a large energy for swinging a large opening / closing body into electricity.

97, 99, and 100, the large opening / closing body is an open / closed body W that is perpendicular to the tide flow and is open and open in parallel with the tide flow even when a strong force acts on the opening / closing body W. Even when the force acting on the body W is weak, the force acting on the movement of the cam wheel B or the carriage KAA is approximate, and the cam wheel B or the carriage KAA regardless of the angle at which the opening / closing body faces the tide flow. In FIGS. 97, 99 and 100, the force acting on the movement of the open / closed body is rotated when the open / close body W is used as a generator so that the open / close body W can be erected with a constant force from the beginning to the end. Throughout the entire process, a constant rotational force can be extracted from the cam wheel B or the carriage KAA.

The shape of the sliding surface K shown in FIGS. 97 and 98 is a vortex, but the local portion approximates an arc. 101 (a) and 101 (b) show that the sliding surface K moves along with the movement of the wheel B, and the “intersection angle between the cam wheel rotating body Jg and the stream line standing on the sliding surface K depends on the position of the wheel B. The design is such that Θf ”changes. The virtual point Q is the center of the arc of the sliding surface K, and the action line of “the force Fb that the wheel B presses the sliding surface K” is “the contact point b between the wheel B and the sliding surface K” and the wheel. It passes through the rotation axis Ib and the virtual point Q.
101 (a) and 101 (b), the rotation axis Ib of the wheel moves circularly around the imaginary point Q. Therefore, FIGS. 101 (c) and 101 (d) show the cam wheel rotor Jg of FIGS. 101 (a) and 101 (b). In place of the sliding surface K, a "rotating body J that rotates about a fixed support shaft Sw provided on the fixed portion W" and a link A connected to the rotating body J and connected to the lid D are attached, The “force Fb that the wheel presses the sliding surface” shown in 101 (a) and 101 (b) acts on the axis of the rotating body J and acts on the fixed support shaft Sw.

101 (a) and 101 (b) show that the sliding surface K of the circular arc can be moved without being fixed, and the “intersection angle Θf between the cam wheel rotating body Jg and the normal line standing on the sliding surface K” is slid. The wheel B slides while adjusting the position of the sliding surface K according to the position of the wheel B on the moving surface K, the opening degree of the lid D, or the moment of the force acting around the pivot axis O of the lid D. A rotation mechanism that moves along K and rotates the lid D. The direction of the line of action of the pressing force Fb is a desired direction according to the position of the wheel B on the sliding surface K or the opening of the lid D. Can be designed. As an example of the movement of the sliding surface K described above, it is also conceivable to rotate about a fixed support shaft on which the sliding surface K is not fixed.
Similarly, in FIGS. 101C and 101D, the rotation axis Sw of the rotating body J is attached so as to be movable, and the “intersection angle Θj between the axis line Zj of the rotating body J and the axis line Za of the link A” is adjusted. FIG. 6 is an operation explanatory diagram of a rotation mechanism in which the lid D is rotated about the pivot O. The rotating shaft Sw of the rotating body J is attached to a slider that moves along a groove (not shown) provided in the fixed portion W.

FIG. 101 (a) is an operation explanatory diagram in which the lid D and the cam wheel rotating body Jg shift from an orthogonal state to an overlapping state. As the wheel B approaches the rotation axis Q along the sliding surface K, the cam wheel The intersection angle Θf between the rotating body Jg and the line of action of the force Fb increases.
FIG. 101 (b) is an operation explanatory view after moving the sliding surface K, and the rate at which the intersection angle Θf increases is small.
In this way, the crossing angle Θk is made as constant as possible according to the position of the cam wheel by moving the sliding surface K without being limited to rotation. Alternatively, the cam wheel rotating body Jg can be translated in a vertical manner, for example.
What can be said about FIGS. 101 (a) and 101 (b) is also true of FIGS. 101 (c) and 101 (d), and FIGS. 101 (c) and 101 (d) correspond to FIGS. 101 (a) and 101 (b), respectively.

FIG. 102 shows the operation of the apparatus for generating power by causing the gate D to rotate in the direction opposite to the arrow B in the figure by the water flow A in the direction of the arrow A in the figure, and to transmit the rotation of the axis O to the generator R. FIG.
FIG. 102 (a) employs the rotating mechanism of FIG. 35 as the moving means of the gate D, and rotates the gate D in the direction of the arrow B in the figure against the water flow a.
The cam wheel rotating body Jg rotates around the “connection shaft C provided at the gate D”, and the wheel B rotates along the sliding surface K in the direction of arrow C in the figure.

The wing W attached to the gate D rotates in the direction of the arrow D in the figure around the support shaft S provided on the gate D so that the water flow a passes through the gate D.
The blade W swings between a closed position where the blade W comes into contact with the contact G1 shown in FIG. 102A and an open position where the blade W comes into contact with the contact G2 shown in FIG. The sliding surface K is rotatably supported around the rotation axis Q. The sliding surface rotates by rotating the shaft Sg in the direction of the arrow in the figure while the contact GG moves along the sliding surface K. Rotate K in the direction of arrow E in the figure. When the gate D rotates in the direction of arrow B in the figure against the water flow, the sliding surface K is stationary at the position shown in FIG. 102A, and the gate D is moved in the direction opposite to the arrow B in the figure by the water flow. When rotating, the sliding surface K stops at the position shown in FIG.

A gate Di, a connecting shaft Ci, a cam wheel rotating body Jgi, and a wheel Bi (i20, 1, 2, 3) indicated by broken lines in FIG. 102 (a) are positions in the course of rotating the gate D in the direction indicated by an arrow B in the figure. In this figure, the water pressure in the direction indicated by the arrow a in FIG. 3 is increased as the gate D moves from the position D0 to the position D4, and the sliding surface is at the position D0 where the water pressure is minimum. The blade W is rotated in the direction indicated by arrow E in the figure, and the blade W is rotated in the direction indicated by arrow D in the figure.
As shown in FIG. 102 (b), when the blade W is in the closed position and receives the pressure of the water stream A, the gate D rotates in the direction opposite to the arrow B in the figure to generate electric power. The sliding surface K rotates in the direction opposite to the arrow in the figure in the direction opposite to the arrow GG in the drawing so that the wheel does not resist the rotation of the gate D in the direction opposite to the arrow B in the figure. ing.

The door opening and closing device of the present invention is such that the force for rotating the door before closing is insufficient, and the line of action of the force acting on the door passes through the vicinity of the pivot axis O of the door. This not only reduces the “distance Lf between the force line of action and the center of rotation”, but also places a large load on the door pivot O, increasing the rotational resistance around the door pivot O, Friction is also supposed to occur.
In addition, the door opening and closing device of the present invention is a link device that is difficult to move immediately before closing, and the rotational resistance around the connecting shaft of the link constituting the link device is increased, which causes friction.
In this way, the force F acting on the pivot axis O of the door acts in the direction of pulling the door and the door frame away from each other, and as shown in FIG. 103, the “gap d between the door D on the latch side and the door frame W” is increased. Narrowing it will distort the door. When the gap d is widened as shown in FIG. 103 (a), it is easy to close, and when the gap d is narrowed as shown in FIG. 103 (b), it is difficult to close.
Each time the door is used, the door hinge O1 is worn or loose around the door hinge mounting bolt, and the distortion of the door shown in FIGS. 103 (a) and 103 (b) increases. In order to prevent such a result, it is desirable that the door hinge O1 and the closing device are not separated but integrated as shown in the figure.
Figure 103 (a) (b) is a elevational view of the switchgear attached to outdoor, (c) (d) are operation explanatory plan view.
Whether the force F acting on the door pivot O acts in the direction of pulling or pulling the door and the door frame depends on whether the switchgear is installed indoors or outdoors, and also depends on whether the biasing means is compression or tension, It also differs depending on the attachment position of the connection shaft C and the fixed support shaft Sw. When installed outside the room as shown in FIG. 103, it does not interfere with passers-by, but when installed indoors, the device is in the passage, so the space in the passage is narrowed.
104 and 105 show an embodiment in which the device is mounted on the indoor side, and the mounting portion closer to the pivot O of the door of the device revolves away from the pivot O of the door than when mounted on the outdoor side. by adopting the movable pulley and the cord in Fig. 104, it is loosened by increasing the length of the arm link in Figure 105 a.

104 to 109 are “rotational control mechanisms that convert the inertial force that attaches to the door just before closing into a braking force”, and conform to the speed reducer described in FIGS. 6, 44, 63, 72, and 78.
The closing device of the present invention does not have the force to seal the door at the end of the range (a), and does not have the force to rotate while closing the door. In this case, if the rotation of the driven body stops, the rotation of the closing device also stops and does not seal. In order to achieve sealing, the “switching means” is operated before the latch abuts against the door frame W to switch from the force to rotate the door to the sealing force, or to the door if it does not switch to the sealing force. It must be either helped by inertial force. In either case, the door accelerates just before closing.
It is ideal to start the sealing work when the door is stopped, or start the sealing work while decelerating. At the end of the range (a), the sealing work is started with no force to seal the door. To do so, the closure device must continue to rotate independently without transmitting the rotation to the door.

The closing device of the present invention is an expansion joint that is inserted between a driven body and a fixed portion, and both ends of the closing device are connected to the driven body and the fixed portion. One end of the closing device is a drive shaft, and the other end is, for example, a spring support shaft in the case of FIGS. 3 to 5, and a sliding surface and a wheel in FIGS. , 50 is a link support shaft. When both ends of the closing device are connected to the driven body and the fixed portion without providing play, the operation of the closing device is rotation of the driven body without play. In other words, when the rotation of the driven body stops, the closing device also stops rotating.
When both ends of the closing device are provided with play so as to be connected to the driven body and the fixed part, the operation of the closing device may or may not rotate the driven body due to play. In other words, even if the rotation of the driven body stops, the closing device does not stop rotating.

One of the fulcrum supporting the sealing force at the time of sealing is the drive shaft, and the other is the “sliding surface and wheel of the sealing device” or the link support shaft. Therefore, if the play is provided in at least one of the drive shaft, “sliding surface and wheel of the sealing device”, and the link support shaft, the rotation of the closing device does not stop even if the rotation of the driven body stops.
In the case of FIGS. 3 to 5, the drive shaft, the working support shaft, the working support shaft, the sliding body, and the wheel are attached so as to be movable. In the case of Fig. 13, the drive shaft and the sliding surface, and in Figs. 13 and 50, the drive shaft and the link support shaft.
47 and 72, the drive shaft is rotatably attached to the door. In FIG. 57, the sliding surface is rotatably attached to the door. In FIG. 74, the wheel is rotatably attached to the door frame. 50 and 51, the working support shaft is rotatably attached to the door. In FIG. 82, the upper limit of the full opening angle is expanded by attaching the drive shaft to the door so as to be rotatable. In FIGS. 34 and 82, the magnitude of the force acting on the door is adjusted by moving the drive shaft.

FIG. 104 shows an embodiment in which a closing device that is attached to the outside of the door of the outward door shown in FIG. 19 is attached to the indoor side. FIG. 104 is a plan view for explaining the operation, and FIG. , (B) to (d) show the state of the door just before closing, and (e) shows the state of the door when sealed.
A connection shaft C is provided at the upper portion of the door surface, and a bearing Sz is rotatably supported around the connection shaft C. The bearing Sz includes through holes Sh and Shh through which the shafts Sf and Sff pass. The shafts Sf and Sff reciprocate through the through holes Sh and Shh without rotating in the axis Z direction in parallel with the door surface.
Wheels Bf and Bb are attached to both ends of the shaft Sf, a pulley B1 is attached to one end of the shaft Sff near the door pivot O, and a push spring U between the other end far from the door pivot O and the bearing Sz. Is installed. The shaft Sff is biased in a direction away from the pivot axis O of the door along the axis of the through hole Shh, and the shaft Sf is biased in a direction away from the axis of the through hole Sh.

A passage body having a long hole Hf is attached to the ceiling surface on the indoor side, and the wheel Bf attached to the tip of the shaft Sf is accommodated in the long hole Hf. In the long hole Hf, there are provided a start end Hf1 close to the pivot axis O of the door and a far end Hf2, between which the wheel Bf can reciprocate, and a groove continuous to the start end Hf1 is provided. And a groove continuous to the end Hf2 is provided, and the groove is substantially parallel to the closed door surface. Even if the wheel Bf can move in the length direction of the groove, movement in the width direction is prevented. Then, the wheel Bf is restrained to the position of the start end Hf1 at the time of opening shown in FIG.
If the contact Gsz provided on the bearing Sz immediately before closing in FIG. 104 (b) abuts against the door surface and the door continues to rotate, the wheel Bf leaves the position of the starting end Hf1 and ends as shown in FIG. 104 (e). Moves to the position of Hf2.
Since the shaft Sf is urged away in the direction along the axis of the through hole Sh and moves in the direction of arrow A in the figure, the door D rotates in the direction of arrow B in the figure about the pivot axis O of the door.

When the door closing device for the outside door is attached to the indoor side, the position where the wheel Bf is fastened is farther from the door pivot O on the indoor side than when the door is attached to the outdoor side, and the wheel Bf attached to the tip of the shaft Sf is Since it moves including the outdoor range, the movement of the shaft is large from the time of full opening to the time of closing. The length of movement of the shaft Sf along the axis of the through hole Sh is half of the length of movement of the pulley B1, and the use of a moving pulley reduces the expansion and contraction of the spring.

As shown in FIG. 104 (a), the spring force acts on the “position of the starting end Hf1 near the pivot axis O of the door” in the range from fully open to immediately before closing, and even if the spring force is large, the door force is small. Rotate with. It is inherited from “the operation of rotating the door” immediately before the closing to “the operation of pressing the door against the door”, and as shown in FIG. 91 (e), the wheel Bf is attached to the shaft Sf in the range from immediately before closing to the sealing. Bb attached to the opposite side of “the door is strongly sealed by pressing the sliding surface rotating body Jk provided at a position far from the pivot of the door.

The shaft Sf includes a rotation axis Ia of the link A, and the link A is rotatably supported around the rotation axis Ia and is urged by a pulling spring V. A wheel B2 is mounted on a rotating shaft Ib provided at the tip of the link A, and the wheel B2 moves along with the shaft Sf along the sliding surface Kb provided on the shaft Sf. The sliding surface Kb includes a surface Kb1 parallel to the axis of the shaft Sf and a concave surface Kb2, and when the wheel B2 moves along the former in the range from the fully opened state to the immediately before closing state shown in FIG. A force that moves the shaft Sf in the axial direction is strong when moving along the latter in the range from immediately before closing shown in FIG.

The sliding surface rotating body Jk is pivotally supported so as to swing between “a stationary position abutting against the contact G1” and “a stationary position abutting against the contact G2” about the rotation support shaft Ij attached to the ceiling surface. With the toggle spring, the contact comes into contact with G1 in the range from fully open to immediately before closing (A), and stops in contact with G2 in the “range from immediately before close to closed (yes)”.
At the closing time shown in FIG.
The force that the wheel B2 moves parallel to the door surface is supported by the force Fb that the wheel Bb presses the sliding surface Kj and the force that strongly presses the door against the door, and the wheel B2 is caused by the so-called wedge effect. The force that presses the sliding surface Kb2 is decomposed into a strong force in a direction substantially perpendicular thereto. In addition to this effect, the distance Lb between the action line Fb of the “force for rotating the door” and the pivot axis O of the door is increased, so that the door is strongly pressed against the door.

In the sealing device of FIG. 104, when the sliding surface is rotatably or movably mounted, the intersection angle between the sliding surface and the moving direction of the wheel moving along the sliding surface changes, so that the wheel stops or decelerates. I have to.
In the process during which the wheel Bf shown in FIG. 104 (b) leaves the position of the starting end Hf1 and the wheel Bf shown in FIG. 104 (e) moves to the position of the terminal end Hf2, the door closing speed is reduced. However, when the door rotates rapidly due to an external force such as strong wind acting on the door, it has a “function of temporarily stopping the door immediately before closing”.
The closing device of FIG. 104 is designed so that the force of the push spring U is weakened in the range from immediately before closing to sealing, there is no force to rotate the door, the door continues to rotate with dynamic inertia, and the wheel Bf is separated from the starting end Hf1. ing.

As shown in FIG. 104 (b), when the wheel B2 comes into contact with the sliding surface K attached to the ceiling surface, the sliding surface rotating body Jk rotates about the connecting shaft C in the direction of the arrow C in the figure, and the wheel Bf Is separated from the starting end Hf1, the shaft Sf moves in the direction of the arrow A in the figure, and the wheel B2 moves along the concave surface Kb2.
At this time, the greater the inertial force attached to the door, the greater the rotation of the sliding surface rotating body Jk about the connecting shaft C. As shown in FIG. 104 (c), “Bb attached to the shaft Sf on the opposite side of the wheel Bf”. Moves to “a position far from the rotation axis Ij of the sliding surface rotating body Jk”.
The sliding surface Kje at the “position far from the rotational axis Ij of the sliding surface rotating body Jk” is a convex surface, and the more the wheel B is away from the rotational axis Ij, the more “the sliding surface Kj and the shaft core line Zsf of the shaft Sf The crossing angle Θa "approaches a right angle from an acute angle, and the wheel B is difficult to return in the direction of the rotation axis Ij.
The connecting shaft C is located between the “point bbf where the wheel Bf is supported by the long hole Hf” and the “point bk1 where the wheel B2 is supported by the sliding surface K1”. Even if it tries to rotate in the direction, it is blocked and does not seal.

As shown in FIG. 104 (d), the force is not applied to the push spring U, the wheel B2 moves along the concave surface Kb2, and the shaft Sf moves in the direction of arrow A in the figure. When the force Fb for pressing the moving surface Kj "is in the region closer to the door than the rotation axis Ij, the sliding surface rotating body Jk is prevented from rotating in the opposite direction to the arrow H in the figure by the contact Gj2. The wheel Bb moves along the sliding surface Kj in the direction of the arrow D in the figure, and the bearing Sz rotates about the connecting shaft C in the direction opposite to the arrow C in the figure, so that the contact Gsz contacts the door surface and the door D and the bearing Sz are relatively integrated.
When the wheel B2 moves simultaneously on the sliding surface Kb2, the wheel Bb moves on the sliding surface Kj, and the wheel Bf moves on the sliding surface Kf in the long hole Hf. It is converted into braking force in proportion to the magnitude.
Although the door D rotates in the direction indicated by the arrow B in the figure by the force Fb of the wheel Bb pressing the sliding surface Kj, the door does not rotate in the opening direction as in the case of FIG. The sealing device of FIG. 104 seals while maintaining a state that does not lead to sealing at a stretch.

When the wheel Bb moves on the sliding surface Kj and reaches the concave portion of the sliding surface Kj, as shown in FIG. 104 (e), “the force Fb that the wheel Bb presses the sliding surface Kj” is generated from the rotation axis Ij. In the region far from the door, the sliding surface rotating body Jk rotates in the direction indicated by the arrow E in the figure, and moves away from Gj1 to stop rotating in the direction indicated by the arrow H by the contact Gj2.
When opening the closed door, the wheel Bb moves on the sliding surface Kj and contracts the push spring U. However, since the sliding surface rotating body Jk can rotate in the direction opposite to the arrow H in the figure, the door begins to open. There is little resistance. When the sliding surface rotating body Jk rotates and hits Gj2 and enters the state shown in FIG. 104 (d), the wheel B can be returned to the starting end Hf1 by further opening the door. A range in which the wheel Bb can move to a position farthest from the rotation axis Ij of the sliding surface Kj while the contact Gsz is in contact with the door surface and the wheel Bb is on the sliding surface Kj. Then, even if the hand is released, the door can be sealed in the state shown in FIG.

The opening degree of the door when the wheel B is returned to the starting end Hf1 when the door is opened is obviously larger than the opening degree of the door when the wheel B is separated from the starting end Hf1 when the door shown in FIG. 104 (b) is closed. That is, when the door is closed, the door is decelerated, and the door rotates with inertial force.
Thus, the force required to seal the door can be reduced by using the inertial force when sealing the door, and the force required to start opening the closed door can be reduced.

105 is a plan view for explaining the operation when the opening / closing device shown in FIG. 6 attached to the indoor side is attached to the indoor side. FIG. 105 (a) is when fully opened, FIG. 105 (b) is immediately before closing, FIG. c) shows the closed state.
When attached to the indoor side as shown in FIG. 105 (b), the distance Lb from the pivot axis O of the door to the action point b is equal to or greater than “the sum of the thickness of the door and the half of the wheel diameter of the wheel B”. It is larger than the revolution radius of the point of action b when it is attached to the. Accordingly, the length of the rotating body J with the wheel B attached to the tip is lengthened, the total rotation angle of the rotating body J is reduced, and the rotational force M acting around the rotation axis Sw of the rotating body J is transmitted small. I have to.
105 (a), (b), and (c) respectively explain "rotating means in the range of (A)", "switching means", and "rotating means in the range of (I)". The wheel B moves in the direction of arrow C in the figure along the sliding surface K fixed to the door D, and the door D rotates in the direction of arrow B in the figure around the pivot axis O of the door.
The sliding surface K includes a passage of the wheel B that moves away from the vicinity of the door pivot O, and the wheel B is furthest away from the door pivot O when sealed as shown in FIG.

The tension spring V has one fulcrum attached to the support shaft Sv provided on the door frame W, and the other fulcrum provided at the tip of the “link A rotating about the connection shaft C provided in the intermediate part of the rotating body J”. Attach to the spindle Sa.
As shown in FIG. 105 (a), in “range (A)”, the rotation of the link A in the direction of the arrow D in the drawing is stopped by the contact Gj, and the axial center line of the tension spring V is shown in FIG. When A crosses the rotation axis C of the link A, the link A moves away from the hit Gj, and the rotation of the link A in the direction of the arrow D in the drawing is stopped by the hit Ga as shown in FIG.

105 (a) to 105 (c) show that when the wheel B presses the position farthest from the pivot axis O of the door of the sliding surface K and the pulling spring V is farthest from the fixed support shaft Sw when sealed. The force is acting on the door as much as possible.
105 (d) to (f) are substantially the same as (a) to (c), and the wheel BB is attached to the end opposite to the end to which the wheel B of the rotating body J is attached. The shape of K is different. The illustration of the means for generating the rotational force M acting around the fixed support shaft Sw is omitted. As shown in FIG. 105 (f), the wheel B becomes ineffective when sealed, and the wheel BB works effectively by pressing the sliding surface KK2. FIGS. 105D to 105F are obtained by attaching the opening / closing device of FIG. 72 on the indoor side, and are the same as the rotation mechanism of FIG. 19 relayed from the rotation device to the sealing device.
105 (d) to 105 (f) are explanatory views of the operation before and at the closing time, and the sliding surface KK2 is the sliding surface of the cam body KK that rotates about the connecting shaft CC provided on the door D. A radial surface KK0 is provided in the radial direction from the vicinity of CC, and a peripheral surface KK2 is provided continuously from the start end KK1 to the end KK2 in the circumferential direction. FIG. 105 (d) shows the end of “(A) range” and the beginning of “(I) range”. This is the moment when the wheel BB contacts the sliding surface KK.
The “force Fbb that the wheel BB presses the sliding surface KK” rotates the cam body KK in the direction of the arrow E in the figure, and a gap BK is created between the radial surface KK0 and the door surface D0. The circumferential surface KK2 is a spiral curved sliding surface that decreases in distance from the connecting shaft CC as it approaches the starting end KK1, and the wheel BB moves along the sliding surface KK2 in the direction indicated by the arrow in FIG. Fit. FIG. 105 (f) is a state diagram at the time of sealing. The rotation of the cam body KK in the direction of the arrow in the drawing is blocked by the contact Gk, and the door surface D0 is brought into close contact with the door contact Gd by the pressing force Fbb.
As shown in FIG. 105 (d), when the wheel BB contacts the peripheral surface KK2, when the inertia force is attached to the door, friction is generated between the wheel BB and the peripheral surface KK2 by the pressing force Fbb, and the wheel BB Does not move on the peripheral surface KK2, and instead, the cam body KK rotates in the direction opposite to the arrow direction in the figure, and the gap BK is eliminated as shown in FIG. 105 (e). When the radial surface KK0 comes into contact with the door surface D5, the wheel BB moves toward the starting end KK1 and reaches the starting end, and enters between the radial surface KK0 and the door surface D0 as shown in FIG. 105 (f). And then sealed. When the inertial force attached to the door disappears before the wheel BB moves and reaches the start end KK1, the rotation of the door stops, the cam body KK is rotated in the direction of the arrow in the figure by the above pressing force, and again shown in FIG. As shown in d), a gap BK is created. Thus, the wheel BB follows different movement paths depending on the magnitude of the inertial force attached to the door immediately before closing, and the sealing device takes a different form. That is, the amount of rotation of the cam body KK varies depending on the magnitude of the inertial force, and the inertial force acts as a rotational resistance of the cam body KK and is converted into a braking force that acts on the door.

FIG. 106 is a diagram in which the sliding surface K is movably attached to the door D in place of the sliding surface K2 of the opening / closing device of FIG. 15, and the sliding surface K is around the connecting shaft P provided at the tip of the link A. It is pivotally supported by the shaft. The link A is rotatably supported around a connection axis Ca provided on the door D.
FIG. 106A shows the end state of “rotating means in the range (A)” by a dotted line, and shows the beginning of “rotating means in the range (A)” by a solid line. A dotted line indicates a state in which the tip of the sliding surface K does not contact the door frame W, and the pulling spring Va biases the sliding surface K so that the sliding surface K rotates about the connecting shaft P in the direction of arrow B in the figure. Thus, the link A and the door surface are in close contact with each other. The rotation of the sliding surface K in the direction indicated by the arrow B in the drawing is blocked by G.
The solid line shows a state in which the tip end bk of the sliding surface K abuts on the door frame W, and the link A rotates in the direction of arrow A in FIG. When the front end bk of the sliding surface K comes into contact with the door frame, the revolution of the connecting shaft P around the door pivot O stops, and the door D rotates with the inertial force attached to the door regardless of the operation of the device. to continue. The urging force of the tension spring V is not only involved in the rotation of the door, but also resists the rotation of the door by the extension of the tension spring V slightly.
Also, before and after the front end bk of the sliding surface K abuts against the door frame, when the axial center line Zv of the tension spring V crosses the connecting shaft P, the rotating body J rotates about the connecting shaft P in the direction indicated by the arrow C in the figure. Begin to.

As shown in FIG. 106 (b), the greater the “inertia force attached to the door before closing”, the greater the link A rotates, and the “intersection angle Θa between the axis A of the link A and the door surface” increases. As the intersection angle Θa increases, the “intersection angle Θk between the sliding surface and the door frame” approaches a right angle, the resistance when the rotating body J moves along the sliding surface K increases, and the rotation of the rotating body J increases. Become slow.

As shown in FIG. 106 (c), when the rotator J further rotates in the direction of arrow C in the figure about the connecting shaft P, the sliding surface K rotates in the direction opposite to the arrow B in the figure about the connecting shaft P. Then, the link A rotates in the direction of arrow A in the figure around the connection axis Ca. In this process, the wheel B moves in the direction approaching the door pivot O, the tip bk of the sliding surface K moves away from the door pivot O, and the connecting shaft P is centered on the door pivot O in the figure. Move the direction and rotate the door.
The wheel B moves in a direction approaching the door pivot O, and the tip end bk of the sliding surface K moves away from the door pivot O, and the wheel B moves along the sliding surface K as “the connecting shaft which is the center of rotation”. It moves from a position far from P toward a near position.

The “force Fb that the wheel B presses the sliding surface K” is transmitted to the connecting shaft P and the tip end bk of the sliding surface K, the former rotates the door in the closing direction, and the latter presses the door frame W to open the door. Resists closed rotation.
The farther the wheel B is from the center of rotation P of the sliding surface K, the weaker the force to rotate in the closing direction and the stronger the resisting force. The greater the “inertial force attached to the door just before closing”, the greater the door rotates, and the greater the distance between the connecting shaft P and the wheel B, the weaker the force that rotates the door.
That is, a measuring means for measuring the “inertial force attached to the door just before closing” by the magnitude of the crossing angle Θa and means for converting the inertial force into a braking force according to the magnitude of the inertial force are provided.
When the wheel B moves toward the position closer to the connecting shaft P in this way, the sliding surface K becomes substantially parallel to the door frame W as shown in FIG. Most of the “force Fb pressing the moving surface K” is transmitted to the connecting shaft P, and becomes a force that strongly seals the door. The movement of this series of devices increases as the “inertial force that attaches to the door just before closing” increases, and increases the “required time from immediately before closing until closing”.

That is, the opening / closing device of FIG. 106 does not fix the door force transmission means to the door or the door frame, but movably attaches it, thereby making one movement having a one-to-one relationship with the opening of the door. Instead, there is a feature that moves differently depending on the magnitude of the “inertial force that attaches to the door just before closing”. Further, the magnitude of the “inertia force attached to the door just before closing” is evaluated as the magnitude of the movement of the device, and the magnitude of the braking force can be changed according to the magnitude of the inertia force.
A normal device that brakes with a constant force regardless of the magnitude of the `` inertial force that attaches to the door just before closing '' will not apply the brake when a large inertial force attaches to the door just before the closing, and a small inertia force will be applied to the door. However, if the spring is designed to have a large spring strength, the braking force will increase and the door will not be closed. On the other hand, even when the spring is too strong, it is possible to prevent a large impact sound at closing.

In FIG. 107, a sliding surface K is attached to the rotating body J instead of the wheel B of the opening / closing device of FIG. 16, and the wheel B is movable to the door frame W instead of the sliding surfaces K1, K2 of the opening / closing device of FIG. The wheel B is attached to a wheel rotation axis Ib provided at the tip of the link A, and the link A is rotatably supported around a connection axis Ca provided on the door frame W.
The sliding surface K consists of a sliding surface K2 in the circumferential direction and K in a direction substantially perpendicular thereto, and is rotatably supported around a connecting shaft P provided on the rotating body J. The rotating body J is rotatably supported around a connection axis C provided on the door D.
As shown in FIG. 107 (a), the pulling spring V urges the rotating body J in the direction of arrow A in the figure, and prevents the rotation of the rotating body J in the direction of arrow A in the figure by Gj. K is urged in the direction of arrow B in the figure, and the rotation of the sliding surface K in the direction of arrow B in the figure is prevented by Gk. Further, the end of the link A opposite to the wheel B and the door frame W around the connection axis Ca and the door frame W are connected by a push spring U, and the wheel B is stopped at a position close to the door frame W.
FIG. 107 (a) shows a state where the tip end bk of the sliding surface K does not come into contact with the door frame W at the end of the “rotating means in the range (A)”, and FIG. 107 (a) shows the state in which the front end bk of the sliding surface K is in contact with the door frame W at the beginning of the rotation means ", and 107 (a) shows that the base end K1 of the sliding surface K pulls the wheel B toward the connecting shaft P when sealed. The door is sealed.

When the front end bk of the sliding surface K abuts on the door frame W as shown in FIG. 107 (b), the revolution of the connecting shaft P around the door pivot O stops, and the door D Regardless of the inertia force attached to the door, it keeps rotating. The biasing force of the tension spring V is not only involved in the rotation of the door, but also resists the rotation of the door by extending the length of the tension spring V.
Since the sliding surface K is prevented from rotating in the direction indicated by the arrow B in the figure by the contact Gk, the rotating body J is rotated around the connection axis C in the direction opposite to the arrow A in the figure while being pressed by the wheel B.
When the axial center line Zv of the pulling spring V crosses the connecting shaft P before and after the front end bk of the sliding surface K contacts the door frame, the sliding surface K is opposite to the arrow B in FIG. Start rotating in the direction.
The larger the “inertial force that attaches to the door just before closing” is, the larger the rotating body J rotates in the opposite direction to the arrow a in the figure, and the “intersection angle Θa between the axis A of the link A and the door surface” is perpendicular to the obtuse angle. Decrease significantly.
The rotating body J that has been greatly rotated in the direction opposite to the arrow A in the figure is pulled back by the pulling spring V, and the rotating body J and the sliding surface K are relatively integrated with each other and rotated in the direction of the arrow A in the figure. The wheel B is moved along the sliding surface K2 in the direction approaching the connecting shaft P by the force Fb of the moving surface K pressing the wheel B. The connecting shaft P moves in the direction of arrow E in the figure around the pivot axis O of the door to rotate the door.
As the intersection angle Θa approaches a right angle from the obtuse angle, the gradient when the wheel B moves along the sliding surface K becomes gentler, and the speed at which the sliding surface K moves along the wheel B becomes slower. That is, the greater the “inertial force that attaches to the door just before closing”, the greater the braking force.

When the connecting shaft P or the connecting shaft C is on the side close to the door frame W with the axis core line Zv of the pulling spring V as a boundary, the pulling spring V moves the sliding surface K in the direction opposite to the arrow lot in the drawing or the rotating body J Is urged to rotate in the direction of arrow A in the figure. When the axial center line Zv of the pulling spring V crosses the connecting shaft P before and after the front end bk of the sliding surface K contacts the door frame, the sliding surface K is opposite to the arrow B in FIG. The rotation body J rotates in the direction opposite to the arrow a in the figure, so that the axial center line Zv of the tension spring V does not cross the connecting shaft P. By providing, rotation of the tension spring V around the fixed support shaft Sw is prevented at a predetermined opening of the door. In this way, when the pulling spring V hits and bends at the contact point bv with Gv, if the door continues to rotate with inertial force, the pulling spring V is stretched and resists rotation of the door.

As shown in FIG. 107 (c), when the inertia force attached to the door disappears, the extended tension spring V contracts and biases the door in the opening direction, but without rotating the door in the opening direction, The rotating body J rotates in the direction opposite to the arrow A in the figure in the direction opposite to the arrow B in the figure away from the sliding surface K from the contact Gk.
When the contact Gj comes into contact with the door frame W and the rotation of the rotating body J in the direction opposite to the arrow a in the drawing is prevented, the wheel B moves along the sliding surface K2 and presses the sliding surface K1. become. When the link A is prevented from rotating in the direction opposite to the arrow C in the figure by the contact Gu provided on the opposite side of the wheel B, the wheel B is stopped, and “the force Fb that the sliding surface K presses the wheel B” It is supported by a stationary wheel B and a connecting shaft P.
Unlike the opening / closing apparatus of FIG. 106, “the force Fb that the sliding surface K presses the wheel B” is supported by the door D and the door frame W while the sliding surface K moves along the wheel B. 106. However, as the “inertial force that attaches to the door just before closing” increases, the “required time from immediately before closing to the closing” increases, and the braking force increases as shown in FIG. It is the same as the opening / closing device.

FIG. 108 shows the opening / closing device of FIG. 50 provided with the speed reduction means of FIGS. 106 and 107. Further, when the door is swung by a strong wind or the like and rapidly rotates, the door is stopped immediately before sealing. Means for Preventing ".
The opening / closing device of FIG. 108 is mainly composed of four rotating bodies, and the rotating body J1 is rotatably supported around a connection shaft C1 provided on the door D, and is urged by a pulling spring V in the direction of arrow A in the figure. Rotation in the direction of arrow A in the figure is prevented by the contact between the rotating body J1 and the door surface.
The rotating body J2 is rotatably supported around a connection shaft C2 provided on the rotating body J1, and the connecting shaft P provided on the rotating body J2 is pulled by the link A. When the connecting shaft C2 is in a range close to the door frame W with the axis line of the link A as a boundary, the rotating body J2 is urged in the direction indicated by the arrow B in the figure, and the rotation in the direction indicated by the arrow B is provided in the rotating body J1. It is blocked by Gj2 when hit.
The rotating body J3 is rotatably supported around a connecting shaft C3 provided on the door D, and wheels B and BB are mounted on both ends with the connecting shaft C3 in the middle. The rotating body J3 is urged in the direction indicated by the arrow C by the pulling spring V3, and the rotation in the direction indicated by the arrow C in the figure is prevented when the wheel BB and the sliding surface K2 provided on the rotating body J2 contact each other. .
The rotating body J4 is rotatably supported around a connection shaft C4 provided on the door frame W, and a wheel B4 is mounted on a rotating shaft Ib of a wheel provided at the tip. Further, the wheel rotation shaft Ib and the connection shaft P are connected by a link A.
The rotating body J4 is urged in the direction indicated by the arrow E in the figure by the pulling spring V4, and the door rotates by the rotation in the direction indicated by the arrow E in the figure.

FIG. 108 (a) shows a state in which the wheel BB is close to the connecting axis C of the sliding surface K2 in a state where the tip end b2 of the rotating body J2 is not in contact with the door frame W at the end of “the rotating means in the range (a)”. Shows the status of stopping at the position.
FIG. 108B shows a state in which the tip b2 of the rotating body J2 comes into contact with the door frame W at the beginning of the “rotating means in the range (i)” and the rotation of the rotating body J2 and the rotating body J4 is stopped. . Since the apparatus keeps rotating with the inertial force without rotating the door, the rotating body J1 apparently rotates in the direction opposite to the arrow A in the figure.
While the rotation of the rotating body J1 is stopped, the connecting shaft C3 revolves in the direction of the arrow D in the drawing along with the rotation of the door, whereby the “angle Θj between the side surface K1 and the door surface D” increases. Since a gap is formed between the side surface K1 of the rotating body J1 and the door surface D, the rotating body J3 biased by the pulling spring V3 rotates, and the wheel BB is far from a position close to the connection axis C of the sliding surface K2. Move towards.

In this state, when the “inertial force attached to the door” disappears and the pressing force acting on the “contact portion between the tip end b2 of the rotating body J2 and the door frame W” disappears, the shaft core of the link A is connected to the connecting shaft C2. Since it is located farther from the door frame W, the rotation of the rotating body J4 is transmitted to the rotating body J2, and the rotating body J2 moves away from Gj2 and rotates in the direction opposite to the arrow A in the figure. Further, when the tension spring V1 in the stretched state is contracted, there is no “gap between the side surface K1 of the rotating body J1 and the door surface D”, and “the force for rotating the door in the opening direction” works. This and the “force for rotating the door in the closing direction” by the rotating body J4 cancel each other, and the door closes while decelerating.
At this time, the wheel BB moves along the sliding surface K2 so as to approach the connecting shaft C2, but at the same time, the loose spring V3 is extended to resist the door closing rotation.
Thus, the larger the “inertia force attached to the door” is, the more “the gap between the side surface K1 of the rotating body J1 and the door surface D” is widened, and the “movement distance on the sliding surface K2 of the wheel BB” is longer. The braking force acting on the door immediately before closing is increased.

FIG. 108 (c) shows a state in which the rotating body J3 rotates greatly in accordance with the magnitude of rotation of the rotating body J1 in the direction opposite to the arrow A in FIG. In this state, even if the “inertial force attached to the door” strongly presses the door frame W via the wheel B, the wheel B is difficult to move on the door frame W and prevents the door from rotating. is there. The door D stops before contacting the door stop Gd.
In both the state shown in FIG. 107 (b) and the state shown in FIG. 107 (c), when the “inertial force attached to the door” disappears, the rotating body J1 rotates as shown in FIG. 108 (d) to close the door. The wheel BB reciprocates on the sliding surface K2, and the wheel B moves along the door frame W in a direction away from the door pivot O. The wheel B and the wheel BB move to a position that does not interfere with the sealing of the door.
When the rotating body J4 further rotates and moves along the sliding surface K4 attached to the door D and presses the portion b4 that is substantially parallel to the door frame W, “the wheel B4 presses the sliding surface K4. The line of action of “force Fb” and the axis core line Z4 of the rotating body J4 are arranged in a substantially straight line, and the door is strongly contacted to closely contact Gd.

FIG. 109 is an example in which a speed reduction device that converts an inertial force into a braking force is added to the opening / closing device of FIGS. 20 and 50, and an inertial force detection device J4 and an inertial force reduction device J3 are added.
The rotating body J1 is rotatably supported around a connection shaft C1 provided on the door D, and rotates in the direction of arrow A in the figure by the bias of the torsion spring UV. A wheel B is attached to one end of the link A and a rotation shaft Ib of the wheel provided at the tip of the rotating body J1. The other end of the link A is connected to a connecting shaft P provided at the tip of the rotating body J2. The rotating body J2 is rotatably supported around a connection axis C2 provided on the door frame W, and the rotation in the direction indicated by the arrow C around the connection axis C2 is prevented by the contact G2. The tension spring V3 has one end attached to the rotating body J2 and the other end attached to the rotating body J3, and urges the rotating body J2 in the direction of arrow C in the figure.

When the connecting shaft C2 and the door frame W are on the same side with the axis core line Za of the link A as a boundary, the rotating body J2 engages with G2 and the connecting shaft P is fixed to the door frame W. The door D rotates in the direction indicated by the arrow B in the figure with the pivot axis O of the door as a force by the link A pulling the connecting shaft P.
As shown in FIGS. 109 (a) to 109 (c), when the door D further rotates and the connection axis C2 and the door frame W are opposite to each other with the axis line Za of the link A as a boundary, the link A The traction force causes the rotating body J2 to rotate in the direction opposite to the arrow C in the figure. When the moment due to the traction force of the link A acting around the connection axis C2 exceeds the moment due to the pulling spring V2 in the opposite direction, the rotating body J2 hits and separates from G2. As a result, as shown in FIG. 109 (c), the rotating body J1 rotates greatly, and the wheel B presses the sliding surface K even though the axial center line of the link A is in the position to rotate the door in the opening direction. The door is sealed by the force Fb ".

The rotating body J3 that connects the other end of the tension spring V2 is rotatably supported around a connecting shaft C3 provided on the door frame W, and the rotation of the rotating body J3 in the direction indicated by the arrow D in FIG. Be blocked.
The rotating body J4 is rotatably supported around a connecting shaft C4 provided on the door D, the wheel BB is mounted on one end with the connecting shaft C4 in the middle, and a contact portion JJ is provided on the other end. It is done. Further, the spring is biased in the direction of the arrow E in the figure by the pulling spring V4, and rotation in the same direction is prevented by the hit G.

FIG. 109A shows a state in which the contact portion JJ is separated from the door frame, and FIG. 109B shows a state in which the door is sealed in a state of being substantially parallel to the door frame.
As shown in FIGS. 109 (b) to 109 (c), as the rotating body J4 rotates in the direction opposite to the direction indicated by the arrow E in the drawing, the wheel BB moves along the side surface of the rotating body J3. Rotating in the direction opposite to the arrow D in the figure, the tension spring V2 is extended, and the moment against the traction force of the link A by the tension spring V2 increases.

In FIGS. 106 to 108, the gradient of the sliding surface K changes with respect to the traveling direction of the wheel B depending on the magnitude of the inertial force attached to the door. In the case of FIG. 109, FIGS. ) Has a one-to-one relationship with the opening of the door, and does not exhibit a form in which the structure differs depending on the magnitude of the inertial force. However, when the rotating body J2 hits and separates from G2 and starts to rotate, it is delayed by the inertial force attached to the door. The greater the inertial force attached to the door, the more the door rotates, and the door frame The rotating body J2 begins to rotate after approaching. In this case, the rotational moment due to the tension spring V2 becomes large, and the rotating body J2 is rotated in a state where the traction force of the link A is insufficient, so that the door closing speed becomes lower.

If the force acting on the door exceeds the maximum static friction force even slightly, the stationary door starts to move, but the kinetic friction force acting on the moved door is slightly smaller than the maximum static friction force and more than the maximum static friction force on the door Will continue to act.
FIG. 110 shows a door in which the force acting on the door decreases when the door starts to move.
FIG. 110 (a) shows the moment when the door starts to move when fully open, with a solid line, and shows the state when the door starts to move slightly with a broken line.
The door D closes and rotates in the direction indicated by the arrow B in the figure with the pivot axis O of the door as the axis. The sliding surface K is rotatably supported around a connection axis C provided on the door, and is urged in the direction of arrow C in the figure by a pulling spring V2.
The rotating body J is rotatably supported around a fixed support shaft Sw provided on the door frame W, and is urged in the direction of arrow A in the figure by a pulling spring V1.
The link A is connected to a connecting shaft P provided at the tip of the rotating body J, and the link AA is connected to a connecting shaft PP provided at the tip of the link A. The wheel B is mounted on a rotating shaft Ib of a wheel provided at the tip of the link AA and moves along the sliding surface K.
The circular motion of the rotating body J is converted into the linear motion of the link A. The link A pulls the connecting shaft C via the link AA, the wheel B, and the sliding surface K, and rotates the door D.

When a large force exceeding the maximum static frictional force is applied to the door D80 that is stopped as shown by the solid line in FIG. 110 (a), the tension spring V2 is stretched and the connection shaft C, the wheel rotation shaft Ib80, the connection shaft Pp80, P80 is all arranged on a straight line.
As shown by a broken line in FIG. 110 (b), the force acting on the door D75 that has started to move is weakened, and the pulling spring V2 contracts to “the straight line Za75 connecting the wheel rotation axis Ib and the connecting axis P” and “the wheel rotation”. A straight line Zk75 connecting the axis Ib and the connection axis C is bent at the wheel rotation axis Ib75. The expansion / contraction amount of the tension spring V represents the magnitude of the “force acting on the door”, and contracts when the inertial force is attached to the door, and expands when the inertial force disappears.
That is, the “force acting on the door” becomes smaller when the door starts to move, and it works more strongly when the door approaches the stop state.

As shown in FIG. 110 (b), when the wheel B remains at the tip KK of the sliding surface K and the door is further rotated, the inertial force is small and a large force acts on the door. As shown in the drawing, the sliding surface K rotates in the direction opposite to the arrow C in the drawing while the pulling spring V2 is stretched, and the axial core line Za45 of the link A moves away from the pivot axis O of the door. When the inertia force is large and a small force is applied to the door, the sliding spring K2 is contracted as shown by the broken line, the sliding surface K rotates in the direction of the arrow C in the figure, and the axis A Za44 of the link A is the pivot axis of the door. Approach O.
The axis of the link A is the “action line of the force acting on the door”. When the inertial force disappears and the door stops, the link between the “action line of the force acting on the door” and the pivot axis O of the door As the distance Lf increases, the magnitude of the force acting on the door increases.

FIG. 110 (c) is a state diagram immediately before closing, and the axial center line Zaa of the link AA always rotates in a direction that tries to coincide with the normal line of the sliding surface K, and the axial line Za of the link A and the connecting shaft PP. Stable in a bent state. On the other hand, the force with which the link A pulls the wheel B tries to make the two axis lines Za and Zaa straight. When the two shaft cores are in a straight line, the traction force of the link A becomes difficult to be transmitted to the door, and the door stops. The gradient of the sliding surface K with respect to the movement of the wheel B becomes gentle as the door rotates, and the wheel B cannot move in the direction approaching the connection axis C unless the door rotates.
When the door stops in this way, the two axial core lines Za and Zaa shift from a straight line to a bent state, and a strong force acts on the door. When the door starts to rotate again in this way, the two shaft cores become straight and the wheel B moves. When the wheel B is in the vicinity of the connecting shaft C in this way, the force of the spring V2 that the sliding surface presses the wheel becomes large, so that the sealing force that acts during sealing is transmitted to the door.

When the door is rotated by the two springs V1 and V2 that interfere with each other in this way, the movement of the apparatus also changes depending on the magnitude of the inertial force attached to the door, and the structural form of the apparatus becomes different. The magnitude of the change in the structure of the device represents the magnitude of the inertial force that attaches to the door, and the device is deformed in such a direction that the force decreases as the door rotates faster, and the force decreases as the door rotates slower. Deforms in a stronger direction. The apparatus shown in FIG. 110 has a self-control function that always applies a force to the door as needed. In this way, the door does not rotate and does not stop.

FIG. 111 is a mechanism for decelerating the “rotating means in the range (A)”, and similarly to FIG. 110, the two springs V1 and V2 interfere with each other, and the operation explanatory plan view of the mechanism for closing and rotating the door is shown. It is. The link A is rotatably supported around a connection axis C provided on the door D, and is urged to rotate in the direction of arrow A in the figure by a pulling spring V2. One end of the tension spring V1 is attached to the fixed support shaft Sw provided on the door frame W, and the other end is attached to Sa provided at the tip end portion of the link A.
FIGS. 111 (a) to 111 (f) are explanatory views of a process in which the door D is closed and rotated around the pivot axis O of the door from the fully opened state, and the axial core line Zv of the pulling spring V1 and the axial core line Za of the link A are in a straight line. And the operation of bending around the support shaft Sa is repeated.

In each of FIGS. 111 (a), (c), and (e), the two axial core lines Zv and Za are in a straight line, and a static frictional force acts on the connecting shaft C. The rotation of the link A around the connecting axis C is blocked and remains blocked, and the door D rotates in the direction indicated by the arrow B in the figure, and FIGS. 111 (b), (d), (f) respectively. ), The two core axes Zv and Za shift to a bent state.
The force of the tension spring V2 and the static frictional force are forces that maintain a bent state, and the force of the tension spring V1 is a force that attempts to return to a straight line.
111 (b), (d), and (f) show a state where the former and the latter are balanced and the rotational resistance acting around the connecting shaft reaches the maximum static frictional force. Further, when the “intersection angle Θa of the two axis lines Zv and Za” decreases, the “distance Lf between the axis line Zv and the connection axis C” increases, and the moment around the connection axis C in the direction indicated by the arrow “a” in the figure. As a result, the rotational resistance acting around the connecting shaft C is much smaller than the maximum static frictional force due to an increase in the moment of force generated by the tension spring V1, and therefore the two axial axes Zv and Za are It returns to a straight line in an instant.
As the door closes, the force of the pulling spring V1 is weakened, but the moment in the direction of the arrow a in the figure is not weakened. Therefore, as shown in FIGS. 111 (b), (d) and (f), the intersection angle Θf Gradually decreases, and eventually the two axial core lines Zv and Za are not bent and the door is closed.
The repetition of such an operation repeats the change of the strength of rotating the door, and becomes remarkable when the force of rotating the door is weak as in the present invention. It is done.

The feature of the present invention is that the "switching means" operates the apparatus largely without using the rotation of the door, but the force of the spring does not require the door to rotate and the apparatus is not loaded. In the no-load state, the spring finishes expanding and contracting in an instant, so the large operation of the “switching means” ends in an instant and there is no deceleration effect. In addition, even if the door acts in the opening direction before the closing dimension as in the embodiment of FIG. 13 or the sealing is prevented before the closing dimension as in FIGS. 44 and 45, the door collides during the closing. Then, after the moment of collision, there is no load and the device rotates at high speed.
In the case where the wheel is sealed while pressing the sliding surface as shown in FIGS. 6, 72 and 78, in the case where the sliding surface decelerates by retreating, the door moves when the retracted sliding surface returns to the original position. The phenomenon of rotating in the direction of opening occurs. The operation of opening and closing again before closing is also meaningful in terms of adjusting the speed of the door during sealing, but the door opens after the sliding surface has been retracted and the door has been decelerated. It is better to move as little as possible.

112 and 113 are plan views for explaining the operation of the speed reducer that absorbs the acceleration just before closing, in which the inertial force acting in the closing direction is received by the spring, and the opening direction of the spring is stored even though the opening force is stored in the spring. It is something that is not allowed to move. Further, the closing motion changes depending on “the magnitude of the inertial force attached to the door just before the closing”, and the brake works strongly when the inertial force is large, and weakly when the inertial force is small. 112 and 113, “the force Fb that the wheel presses the sliding surface” works perpendicular to the door frame W and resists the force that closes the door when the wheel B comes into contact with the sliding surface K. It gradually works parallel to the door frame W and does not resist the force of closing the door. In other words, the restoring force of the tension spring V does not rotate in the opening direction of the door, but only the rotating body J rotates to be sealed.
These sealing devices are characterized in that the rotation of the rotating body J is large with respect to slight rotation of the door, and the distance that the wheel B moves along the sliding surface K is long. However, it is characterized in that a large operation of the closing device is not executed in a no-load state.

112 and 113, the door D is rotated in the direction indicated by the arrow B in FIG. The rotating body J is rotatably supported around a connection axis C provided on the door D, and a wheel B is mounted on the end portion.
The sliding surface K is urged by a pulling spring V in the direction of arrow C in the figure with a fixed support shaft Sw provided on the door frame W as an axis. The rotation of the rotating body J and the sliding surface K in the urging direction is prevented by Gj and Gk, respectively.
112 includes a wheel B and a wheel BB, and each moves along a sliding surface K and a sliding surface KK. The rotating body J shown in FIG. 113 does not include the wheel BB. 112, the sliding surface KK is fixed to the door frame W. In FIG. 113, the sliding surface KK is integral with the sliding surface K and faces each other. In FIG. 113, the drawing spring V2 is not shown.

112 (a) shows the state when the “rotating means in the range of (A)” is finished, and FIGS. 112 (b) and 113 (a) show the state when the wheel B comes into contact with the sliding surface K. The pulling spring V1 crosses the connecting shaft C, the rotating body J hits away from Gj, and starts to rotate in the direction opposite to the arrow A in the figure. The axis core line Zj of the rotating body (straight line passing through the connecting shaft C and the rotating shaft of the wheel) is substantially orthogonal to the sliding surface K, and “the force Fb that the wheel presses the sliding surface” is approximately perpendicular to the door frame W. work.

When the “inertial force attached to the door” is small just before the closing, the sliding surface K hardly rotates as shown in FIGS. 112 (b) and 113 (b), and the wheel B moves to the sliding surface K. And moves in the direction of arrow D in the figure, approaches the center of rotation Sw, and reaches the sealing shown in FIGS. 112 (d) and 113 (e). 112 (b) to (d) and FIGS. 113 (a) to (e) show a series of operations when the “inertial force attached to the door” is large, and the wheel B moves to the sliding surface K immediately before closing. The rotating body J rotates greatly on the sliding surface K, and finally the wheel BB in FIG. 112 (d) and the wheel B in FIG. 113 (e) press the sliding surface KK. The door is brought into close contact with the door stop Gd. In the process in which the sliding surface rotates greatly, the sliding surface K rotates more greatly as the inertia force increases, and the wheel B moves away from the fixed support shaft Sw and moves to the tip of the sliding surface K. At this time, the “intersection angle Θj between the shaft center line Zj and the sliding surface K” shifts to an acute angle with respect to the moving direction D of the wheel B, and the wheel B becomes difficult to move in a direction approaching the fixed support shaft Sw. The tension spring V is also stretched. These are factors that resist the force of closing the door, and sufficiently slow down the door.
112 (c) and 113 (d) are diagrams showing a state in which the extended tension spring V2 starts to contract, and the action line of “force Fb that the wheel presses the sliding surface” is substantially parallel to the closed door surface. And approaches the pivot axis O of the door. That is, the force stored in the tension spring V2 rotates the rotating body J without rotating the door. When the closed door is opened, as shown in FIGS. 112 (d) and 113 (e), the “intersection angle Θj between the axial center line Zj and the sliding surface K” is an obtuse angle toward the wheel B or BB in the moving direction E side. Then, the rotating body J is rotated in the direction of the arrow A in the figure and brought into contact with the contact Gj.

The sealing mechanism of the present invention moves substantially parallel to the closed door surface while the wheel B is slightly rotated during sealing. When the closed door is opened, the wheel B is closed to the closed door surface. Since it moves only in parallel and does not move away from the door frame W, it is difficult to open the door.
As shown in FIGS. 15 and 16, the wheel rotates around a fixed axis, and the lever rotates as shown in FIGS. 59 and 60. Once the wheel starts to move, It moves to a position where it can move more easily, and it will be far away from the door frame by a slight rotation of the door, but the wheel moves a long distance along the door frame when sealed as in the embodiment of FIGS. In this case, the wheel does not become easier to move after moving.
In FIGS. 114 and 115, in order to facilitate the opening of the door in such a case, the sliding surface K is fixed at the time of sealing to receive the reaction force of the sealing force, and after the sealing, the fixing is released to release the sealing force. Is.

Sealing the door eliminates the need for a force to act on the door when the latch is recessed and inserted into the door frame.
114 and 115 show that the operation of the device is continued even after the latch is recessed and the door is brought into close contact with the door stop, and the sliding surface is released, so that the wheel does not resist when the door is opened. Since the sealing force is not applied to the closed door, the door does not require a force at the moment of opening.
FIG. 114 (a) shows the operation of “range from fully open to just before closing (A)” by a broken line, and the solid line shows a state in which the sliding surface K is fixed immediately before closing. FIG. 114 (b) is a plan view for explaining the operation at the time of sealing, and FIG. 114 (c) is a plan view for explaining the operation for releasing the fixation of the sliding surface K after the sealing.

114 is a wheel Bd and a wheel Bb that share the rotation axis Ib of the wheel as shown in FIG. 22, and the former is “supported rotatably around a support shaft Sk provided on the door frame W”. The latter moves along a “sliding surface Kd rotatably supported around a connection axis C provided on the door D”.
The rotating body J is rotatably supported around a fixed support shaft Sw fixed to the door frame W, and is rotated in the direction of the arrow A in the figure by an urging means (not shown). A link A is connected to a connecting shaft P provided at the front end of the rotating body J, and a wheel B is installed on a rotating shaft Ib of a wheel provided at the front end of the link A. In the “range from fully open to immediately before closing (A)”, the wheel B is accommodated in a recess Kdd provided at the tip of the sliding surface Kd, and the sliding surface Kd is shown in FIG. Since rotation in the direction is prevented by the contact Gd, the vicinity of the pivot axis O of the door is rotated in the direction indicated by the arrow B in the figure. The door D also rotates in the same direction about the door pivot O.

As indicated by a solid line in FIG. 114 (a), the wheel B rides on the “sliding surface Kb provided on the door frame W” before closing, escapes from the depression Kdd, and connects to the connecting shaft C along the sliding surface Kd. Move in the direction approaching.
The sliding surface Kd comes into contact with the door frame W, and moves away from the contact Kd and rotates in the direction opposite to the arrow C in FIG. The force Fb by which the wheel B presses the sliding surface Kd is transmitted in a distributed manner to the door D and the door frame W. When the wheel B is at a position far from the connecting shaft C, the force Fb is hardly transmitted to the door. Do not rotate the door.
The “contact point b between the sliding surface Kd and the door frame” approaches the connecting shaft C as the door is closed, and the force Fb is applied to the door when the wheel B is on the far side from the connecting shaft C with the contact point b as a boundary. It works in the direction to open the door and closes the door when it is on the near side. Further, as described above, the wheel B has the two wheels Bd and Bb and moves along the two sliding surfaces Kd and Kw at the same time, so the door does not rotate in the opening direction.

The sliding surface Kw is sandwiched and fixed between the contact Gs and the wheel BB. Around the support shaft Sk, rotation in the direction indicated by the arrow D is blocked by Gs, and rotation in the direction opposite to D is blocked by the wheel BB.
The wheel BB is attached to the tip of the link AA, and the link AA is rotatably supported around a support shaft Sa provided on the door frame W. The link AA is urged by the pulling spring V in the direction of the arrow E in the figure, and rotation in the urging direction is prevented by Ga1. At this time, the axial center line Zaa of the link AA and the sliding surface Kw are orthogonal to each other, and as shown in FIG. 114 (b), when sealed, by preventing the sliding surface Kw from rotating in the direction opposite to the arrow D in the figure, The reaction force of the sealing force can be received. The sliding surface Kd is rotatable around the connection axis C, but when the wheel B is in the vicinity of the connection axis C as shown in FIG. 114 (b), most of the force Fb is transmitted to the door. Strongly seal the door.

The link A includes a contact portion GG that contacts the wheel BB or the link AA as shown in FIG. 114 (b) at the same time as or after the sealing, and the contact portion GG is sealed as shown in FIG. 114 (a). Previously separated from them.
As shown in FIG. 114 (c), the sliding surface Kw is designed so that the movement of the wheel B continues even after sealing, and the link AA is rotated in the direction indicated by the arrow E in the figure by the contact portion GG.
When opening the closed door, if the axial center line Zaa of the link AA is not even perpendicular, the wheel BB approaches the center of rotation Sk along the sliding surface Kw, and the sliding surface Kw is around the support shaft Sk. It becomes rotatable and does not resist the movement of the wheel B when the door is opened. The wheel B moves in the direction away from the connection axis C along the sliding surface Kd, and is accommodated in the depression Kdd while bending the link A and the rotating body J about the connection axis P.

The opening / closing device of FIGS. 114 and 115 rotates slightly around the pivot axis O of the door in the “range from fully open to just before closing (A)”, and “range from just before closing to the time of closing (Yes)”. Then, it is far away from the pivot of the door, and while the door rotates from fully open to fully closed, one wheel moves along the door frame, and the rotating body J and link A are in a straight line when closed. It becomes a flat device that attaches to the door frame or the door surface. 114 is a fixing means capable of releasing the sliding surface Kd from the door surface, but protrudes forward from the closed door surface. 115 (a) and 115 (b) are attached in parallel to the closed door surface of the fixing means shown in FIG. 114. FIGS. 115 (c) and 115 (d) are the fixing means shown in FIGS. 115 (a) and 115 (b). Is composed of two links. The switchgear of FIG. 115 is the same as the switchgear of FIG. 114 except for the fixing means.

115 (a) and 115 (b) are substantially parallel to the door surface where the link AA in FIG. 114 is closed. When the sliding surface Kw shown in FIG. It is orthogonal to the sliding surface Kww fixed to.
FIG. 115 (b) illustrates an operation in which the wheel B rotates the link AA at the time of sealing or after that to move the wheel BB in the direction indicated by the arrow E in the figure to release the fixation of the sliding surface Kw.

115 (c) and 115 (d), the support shaft S1 is provided on the sliding surface Kw, and the support shaft S1 and the “support shaft S2 provided on the door frame W” are connected by two links AA1 and AA2. 115 (c), the two links AA1 and AA2 are straight and stationary to fix the sliding surface Kw, and as shown in FIG. 115 (d), the two links AA1 and AA1 AA2 bends about the intermediate connecting shaft PP to make the sliding surface Kw rotatable.
The two links AA1 and AA2 are attached at one end to the support shaft S1 or S2, and the other ends are connected to each other by a connecting shaft PP. A pulling spring V is attached to the ends of the two links AA1 and AA2 near the supporting shafts S1 and S2, and the pulling spring V is connected in a direction in which the connecting shaft PP approaches the wheel B as shown in FIG. 115 (c). AA1 and link AA2 face each other and are urged to rotate in the direction of arrow E in the figure. The links AA1 and AA2 around the connecting shaft PP are provided with a contact Gaa to prevent the links AA1 and AA2 from being bent, and the links AA1 and AA2 remain stationary in a straight line.
FIG. 115 (d) shows that the link AA1 and AA2 rotate in the direction opposite to the arrow E in FIG. 115 by pressing the link AA1 or AA2 when the wheel B passes through the sealed position of the sliding surfaces Kw and Kd. And the state bent around the connecting shaft PP is shown.

116 is a plan view for explaining the operation of the door closing process and the opening process.
116 (d) is a state diagram at the time of closing, FIGS. 116 (a) to (c) are plan views for explaining the process of closing the door immediately before closing, and 116 (e) to (f) for explaining the process of opening the door. FIG. 116 (f) is a plan view when fully opened. The rotating body J rotates in the direction of arrow A in the figure around a fixed support shaft Sw provided on the door frame W, and the door D rotates in the direction of arrow B in the figure about the pivot O of the door. The connecting shaft P provided at the tip of the rotating body J and the connecting shaft C provided at the door D are connected by two links A and AA, and the two links A and AA are connected by a connecting shaft PP. Wheels B are mounted on the connecting shaft PP. The cam body KK rotates about the rotation axis Ik and swings between a position where it abuts against G1 and a position where it abuts against G2. The cam body KK includes a sliding surface K1 on which the wheel B slides on an outer edge portion and a locking portion K2.
FIG. 116 (a) illustrates the operation in which the wheel B moves along the sliding surface K1 in the direction of the arrow C in the drawing and reaches the locking portion K2 in a state where the cam body KK comes into contact with G1 and is stationary. is doing.

As shown in FIG. 116 (b), the wheel B revolves around the fixed support shaft Sw, but the circular motion of the wheel B moves substantially parallel to the closed door surface or on a circular track approaching the door, so the door is closed. It opens slightly on the verge or is in a pause state. As shown in FIG. 116 (c), at the position where the wheel B moves from the sliding surface K1 to the locking portion K2, “the crossing angle Θa between the axis Zz of the rotating body J and the link A moves while increasing. As shown in Fig. 116 (d), the wheel B fits into the locking portion K2. As shown in Fig. 116 (e), the cam body KK hits and hits G2 with the wheel B still stuck in the locking portion K2. When the door is further opened, the cam body KK comes into contact with G2 and stops, and the wheel B is detached from the locking portion K2. The wheel B is locked. Since the position to be separated from K2 is on the pivot axis O side of the door of the “straight line Z passing through the fixed support shaft Sw and the connecting shaft C”, the door does not become flat.

A Rotating body or arm B Wheel C Circle center D Door or metal fitting G attached to door I Rotating shaft or rotating support shaft K Cam body or cam body sliding surface O Rotating shaft Q of rotating body R Rotating axis R of rotating body S Spring connecting shaft T Vertical line U Spring V Pull spring W Metal fitting or plate to be attached to door frame

Claims (8)

1 or more between the fixed part W, the connecting shaft C provided on the door body D rotatably supported around the pivot O provided on the fixed part W, and the fixed part support shaft Sw provided on the fixed part W A link device is constructed by connecting the link of the link device with a pair or a slip pair, so that the driving rotational force acting around the connecting shaft that is not the pivot axis O of the link device is transmitted, and the rotational force acts around the pivot axis O. In the opening / closing device in which the door D rotates ,
Pivoted to rotatably link A around the upper Symbol connection axis C, and fitted with wheels B to pivot Ib provided at the distal end portion of said link A, sliding which the wheel B is provided on the fixed portion W It moves along the moving surface K so that “the contact point b between the wheel B and the sliding surface K”, the support shaft Ib, and the connection shaft C are arranged in a substantially straight line.
Forces acting in the axial direction of the link A is a substantially tangential direction of the circular movement of the connecting shaft C around the pivot O, and to ensure that is a force in the opposite direction to bias the door body D A speed reduction mechanism for a switchgear. 1 or more between the fixed part W, the connecting shaft C provided on the door body D rotatably supported around the pivot O provided on the fixed part W, and the fixed part support shaft Sw provided on the fixed part W A link device is constructed by connecting the link of the link device with a pair or a slip pair, so that the driving rotational force acting around the connecting shaft that is not the pivot axis O of the link device is transmitted, and the rotational force acts around the pivot axis O. In the opening / closing device in which the door D rotates,
An intermediate portion of the link A passes through a bearing provided in the door body D, and a wheel B attached to a support shaft Ib provided at a tip portion of the link A extends along a sliding surface K provided in the fixed portion W. Like moving,
Forces acting in the cross-sectional direction of the link A is a substantially tangential direction of the circular movement of the connecting shaft C around the pivot O, and to ensure that is a force in the opposite direction for biasing the door body D A speed reduction mechanism for a switchgear. A spring that expands and contracts as the link A rotates around the connecting shaft C is provided, or the sliding surface K is pivotally supported around the fixed portion supporting shaft Sw, and the sliding surface is provided. A spring is provided that expands and contracts as K rotates around the fixed portion support shaft Sw, and the restoring force of the spring is applied in a direction opposite to the direction in which the door body D is rotated by the biasing means. Item 3. A speed reduction mechanism for an opening / closing device according to item 1 or 2. The sliding surface K is rotatably supported around the fixed portion support shaft Sw, and the magnitude of the rotation of the sliding surface K depends on the magnitude of the force with which the wheel B presses the sliding surface K. The speed reduction mechanism for an opening / closing device according to any one of claims 1 to 3, wherein the direction of the force with which the wheel B presses the sliding surface K changes . A fixed portion W, a door body D that is rotatably supported around a pivot O provided on the fixed portion W, and a rotation that is rotatably supported around a fixed portion support shaft Sw provided on the fixed portion W. and body J, and the link a is rotatably supported around the connection axis C provided on the door body D, and the connecting shaft P provided on the connecting shaft PP and the rotating member J provided in the link a A link device is constituted by the link AA to be connected, and the driving rotational force acting around the connecting shaft that is not the pivot axis O of the link device is transmitted, so that the rotational force acts around the pivot axis O, and the door body D Is an opening and closing device that rotates,
When the aforementioned connecting shaft C and the connecting shaft PP and the connecting shaft P is distribution in a substantially straight line, or when the connection shaft PP crosses the "straight line passing through the said connecting shaft C and the upper connecting shaft P",
A speed reducing mechanism for an opening / closing device, wherein a direction of a force for energizing the door body D changes from a closing direction to an opening direction.
Deceleration mechanism for switchgear. 1 or more between the fixed part W, the connecting shaft C provided on the door body D rotatably supported around the pivot O provided on the fixed part W, and the fixed part support shaft Sw provided on the fixed part W A link device is constructed by connecting the link of the link device with a pair or a slip pair, so that the driving rotational force acting around the connecting shaft that is not the pivot axis O of the link device is transmitted, and the rotational force acts around the pivot axis O. In the opening / closing device in which the door D rotates,
One link A of the one or more links is provided with a support shaft Ib, and a wheel B is mounted on the support shaft Ib, and the wheel B is rotatably supported around the connection shaft C. Move along Kd,
A speed reduction mechanism for an opening / closing device, wherein a direction of a force for energizing the door body D changes from an opening direction to a closing direction. 1 or more between the fixed part W, the connecting shaft C provided on the door body D rotatably supported around the pivot O provided on the fixed part W, and the fixed part support shaft Sw provided on the fixed part W A link device is constructed by connecting the link of the link device with a pair or a slip pair, so that the driving rotational force acting around the connecting shaft that is not the pivot axis O of the link device is transmitted, and the rotational force acts around the pivot axis O. In the opening / closing device in which the door D rotates,
One link A of the one or more links is provided with a support shaft Ib, and a wheel B is mounted on the support shaft Ib. The wheel B is installed in the elongated hole Hd provided in the door body D, and in the fixing portion W. Move in the long hole Hw to be installed at the same time,
The inside of each of the long hole Hd and the long hole Hw is provided with two sliding surfaces K facing each other, and the force with which the wheel B presses one of the two sliding surfaces K urges the door body D. The opening / closing device reduction mechanism, wherein the force for pressing the other in the same direction as the force for pressing is opposite to the force for biasing the door body D. The above-described link device that allows the rotational force to work in a range smaller than a predetermined opening of the door body D, and the link device after the link device to allow the rotational force to work in a large range, The opening / closing device reduction mechanism according to any one of claims 1 to 7, wherein the door body D is urged in a closing direction while an operation is inherited from the link device to the subsequent link device .

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