JP2011122427A - Revolution control mechanism for revolving body, and opening and closing device for door or the like using the same - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a door which is not felt heavy when opened, revolves slowly and closes air-tightly, while having a function of fully opening when opened slightly and fully closing when closed slightly, produces little sound of impact upon closing, and stops temporarily so as to prevent fingers from being caught when strong sudden force is applied to the door. <P>SOLUTION: The invention includes a structure for deceleration without the need of oil viscosity resistance nor friction resistance. A closing speed is controlled by varying the direction of the force. The door is revolved with spring force set to the minimum. Even if the door stops immediately before closing, the device continues to revolve so as to increase the spring force to the maximum. The door closes air-tightly via a first door with little sound of the impact. <P>COPYRIGHT: (C)2011,JPO&amp;INPIT

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.

When a door is opened, the spring accumulates force, and when the door is released from the door, the door closes without permission. In addition, there is a problem that the spring force increases as the door is opened, and the closing speed when closing the door increases. In order not to make a loud impact sound when the door is closed, many door closers are "resisting the door by applying resistance" such as frictional resistance or air or oil viscosity resistance, and increase the resistance. If you do this, it will stop the door, and if you make it smaller, it will not slow down, and the `` door closer with a hydraulic cylinder '' will only work in an `` environment where the force of the spring is much higher than necessary and the resistance against this is very large '' This problem is solved. The "door closer with a hydraulic cylinder" is a very large device, and it is misunderstood as if the door does not rotate unless it is a very large force, but in fact it is an operation that requires little force, The “force acting on the door” is less than a few percent of the spring force of the “door closer with a hydraulic cylinder”.
This technology resists the “door that requires little rotating force” and makes it difficult to turn around, and has the “defect that the door feels heavy when the door is opened”.

“The force acting on the door before it closes” only rotates the door, and when the door closes, it does n’t just rotate the door, but also “the latch that attaches to the handle side of the door”
Is accompanied by the work to dent the inside of the door. Therefore, in the present invention, the rotation range of the door is a rotation range from fully open to immediately before closing (hereinafter referred to as “(A) range”) and a rotation range from immediately before closing to fully closed (hereinafter referred to as “(I) range”. ”), And a force of a different magnitude is applied in each range so that an excessive force is not provided to the door.
Patent Document 1 relates to an electric door that makes the magnitude of the rotational force different from the middle of rotation and the last, and the magnitude of the rotational force is controlled by an electrical signal. Electric doors can close passages during a power outage. The driving means and the control means are different from the present application.
There is a clear boundary between the two rotation ranges where forces of different magnitudes work (hereinafter referred to as “switching range”).
And automatically switches from strong to weak or weak to strong,
The feature is that the “magnifying force” suddenly changes.
In the rotating mechanism in which the rotating body rotates by the force F acting around the rotating shaft, between the rotating force M working around the rotating shaft and the distance L between the rotating shaft and the line of action of the force F. The relationship of (M = F × L) is established. However, in the present invention, the force having the different magnitude is expressed as “the magnitude of the rotational force M or the force F is changed by changing the magnitude of the distance L”. The resistance of the spring is not made small by using resistance like the “door closer with a hydraulic cylinder”.

In Patent Document 2, the rack and gears are meshed and the door is decelerated by the load generated at that time. When a gear having a small rotational speed or a gear having a large rotational speed is rotated by a small movement of the rack, the speed ratio is large. The fact that the rotational resistance of the gear becomes larger is utilized. In the present application, the door is decelerated by rotating the door largely by expansion and contraction of a small spring so that the driving force is insufficient, not by the rotational resistance of the gear.
Patent document 3 is a closed door cushioning mechanism in which a spring serving as a restraining force is provided for a spring that urges the rotating body in the closing direction, but applying a restraining force in the direction opposite to the closing direction is merely a force in the closing direction. Is just reduced. The present application does not perform subtraction to reduce the driving force, but performs multiplication to enlarge or reduce the driving force.

"Adopting resistance for the speed reduction means" means that the force acting on the door is reduced by adding a new force in the direction opposite to the direction of rotation of the rotating body and reducing the "force for energizing the rotating body". The result is the same as using a small spring force instead of a large spring force.
The present invention does not bother reducing the force of the large spring by resistance as described above, but uses the “means for moving the action line of the force acting on the door” to apply a large force of the small spring to the door. And it uses a weaker spring than a normal door closer. By adopting bearings positively without using resistance, the door can be rotated efficiently even with a small force, solving the problems of friction resistance performance variation and deterioration, and when opening the door The problem that the door feels heavy was solved.

When the lid whose rotation axis is horizontal rotates up and down, the center of gravity moves in the horizontal direction and the rotational moment around the rotation axis changes. However, Patent Document 4 discloses that the fulcrum and action point are The distance between them changes continuously and gives a rotational force that balances the rotational moment. However, as in the present application, the rotational range can be distinguished into two, and the structure and mechanism of the device is limited to a predetermined boundary. Does not switch.

The present invention relates to a link device in which a “driving unit composed of a plurality of links” is connected to an “opening / closing unit composed of a door and a door frame connected by a pivot”, and has a large opening / closing unit in “(A) range”. The drive part operates small with respect to the rotation, and the drive part operates largely with respect to the small rotation of the opening and closing part in the “(range)”. The latch male part of the door abuts the female part of the door frame. Thus, a slight rotation of the door until the door contacts the door stop is precisely controlled by a large operation of the drive unit.
Patent Document 5 provides a device that cushions an impact when a door is closed by a damper. The rotary damper is directly connected to the door and operates with a small operation when the door is closed. In Patent Document 5, the rotation mechanism does not suddenly change at the end of rotation as in the present application. In the present application, not a small operation of the opening / closing unit, but a large operation of any link of the driving unit is delayed to buffer the impact.

The lid with the horizontal axis of rotation is stationary everywhere, and the balance of force is an issue, and the door with the vertical axis of rotation handles the movement that accelerates when the force balance is broken.
There is no vertical movement of the center of gravity and there is no change in potential energy. A stationary door begins to rotate with a "force slightly above the maximum static frictional force acting around the door pivot". “A force slightly exceeding the maximum static frictional force” works, as the stopped door starts to move from anywhere (hereinafter, the opening degree of the door when the hand is released from the door and starts closing) is called the closing start opening degree. There must be. Once the door starts to rotate, the rotational resistance around the pivot axis of the door becomes a kinetic friction force smaller than the maximum static friction force, and the magnitude is drastically reduced. The doors are accelerating everywhere in the static force balance.

If a small force continues to act on the door, the door will accelerate and the door will rotate at its maximum speed when closed. The present invention operates in the “(A) range” (hereinafter, the “(A) range” operation is referred to as a rotation operation) and operates in the “(A) range” (hereinafter, “( The operation of “range” is referred to as a sealing operation.) It consists of a sealing device and seals while decelerating before and after the “switching range”.
Patent Document 6 is a sealing device having a buffer function that operates only in the “(range)”, and “force acting on the door” is required to operate the device. In the present invention, “the force acting on the door” is just before closing.
This is different from the point that the sealing device of the present application starts from a state where there is no force to rotate the door. In addition, the sealing mechanism is based on a “rotating mechanism including a sliding surface and a wheel that moves along the sliding surface”. Is getting weaker. In the present application, the line of action of the pressing force is gradually brought closer to the rotating shaft of the rotating body so that the spring force weakened to the minimum at the end of rotation is sealed with a large force.

Patent Documents 7 to 11 relate to a “rotating mechanism including a sliding surface and a wheel moving along the sliding surface”, and “a rotating device in which a rotating body relatively rotates around a pair of rotating shafts separated from each other. One rotating body that rotates about one rotating shaft has a sliding surface, and the other rotating body that rotates about the other rotating shaft has a wheel mounted at the tip, and the sliding surface is It is a rotating device that moves while pressing along the wheel or a rotating device that moves while pressing the wheel along the sliding surface.
The rotation mechanism illustrated in FIG. 4 is “the action line of the force that the sliding surface presses the wheel or the action line of the force that the wheel presses the sliding surface” and “the one rotating body or the other rotation. The rotational force acting around the “rotating axis of the one rotating body or the other rotating body” is controlled by controlling the distance to the “rotating axis of the body”. In FIG. 4, the distance between the line of action of the force and the rotation axis of the rotating body is constant so that “a force slightly exceeding the maximum static frictional force” works everywhere in the door.
Patent Document 7 relates to a “door with a spring mechanism”, in which an intermediate portion of the sliding surface is an arc centered on the other rotation axis, a linear portion is provided at the end, and the force that the sliding surface presses. The line of action is the radial direction of the circular motion of the wheel when the wheel is in the middle, the tangential direction of the circular motion of the wheel when the wheel is at the end, and both rotating bodies when the wheel is in the middle Is a rotation mechanism that does not rotate relatively and rotates when the wheel is at the end. The intermediate part of the sliding surface of Patent Document 6 does not rotate the door, and is irrelevant to the problem that the door accelerates.

Axial line of the "rotating member fitted with wheels at the distal end,""the line of action of the pressing force acting between the sliding surface and the wheel" is the "sliding surface and rotating mechanism and a wheel that moves along with it." (hereinafter, referred to a straight line passing through the support shaft at both ends and the axial line.) and is the so as to approximate the state arranged in a straight line, the rotation axis of the rotating member even when a large force in the axial core direction acts The rotational force that works is small. If this feature is used for a door, even if a strong spring force acts in the pivot direction of the door in the “(A) range”, a large force does not act on the opening and closing of the door, and it feels very light when opening the door. Effects.
The present invention also provides a “rotating body having a sliding surface” as a lid whose rotation axis is horizontal, and a rotating mechanism in which the lid rotates up and down by the rotation of the “rotating body with a wheel attached to the tip”. Thus, the lid can be rotated up and down while supporting a large lid weight in the axial direction even if the rotational force acting around the rotation axis of the “rotary body with wheels attached to the tip” is small.

Patent Document 8 relates to "the hinge of a trunk lid of an automobile", and the gravity of the trunk lid acts as a large force in the circumferential direction of the circular motion of the wheel, and the sliding surface counteracts with the force pressing the wheel. This is the reverse of the “rotary body with wheels attached to the tip” of the present application. The present application supports a large force in the radial direction of the circular motion of the wheel and counters it with a small force acting in the circumferential direction of the circular motion of the wheel, and can support a large weight of the trunk lid with a small spring force.
Patent Document 9 relates to a hinge device of a document transporting and accumulating unit of a copying machine that rotates about a horizontal support shaft. The spring of the wheel moves so that the rotating shaft of the wheel moves in a long hole provided in the lid. Acting in the direction of pulling up the rotating shaft, the force of the spring is decomposed into a force that supports the lid through a force slot that presses the sliding surface, and part of the force of the spring is transmitted to the lid.
The change in the magnitude of the force acting on the lid is solely due to the change in the length of the spring to follow, and is not proportional to the distance between the spring axis and the rotation axis of the rotating body.
The “rotary body with a wheel attached to the tip” of the present application corresponds to the document conveying and accumulating unit of the copying machine of Patent Document 9, and the force acting on the door is “the force with which the wheel presses the sliding surface”, The action line is the radial direction of the circular motion of the wheel B. The “force acting on the door” can be adjusted from zero to infinity depending on the distance between the action line and the pivot O, and the spring force does not have to change. Patent Document 9 is an opening / closing device in which the rotation of the lid and the expansion and contraction of the spring are related over the entire rotation range. In this application, the rotation of the door is not the expansion and contraction of the spring but the distance from the pivot O.

Patent Document 10 relates to a “back door support structure”, in which a back door of an automobile is moved up and down by “a damper stay that expands and contracts by air pressure”. The back door weight is supported by a stay that expands and contracts, and the back door is moved up and down by the extension of the stay. The biasing means is a support that supports the weight. The “rotary body with a wheel attached to the tip” in the present application is a rigid body, and the support body that supports the weight does not expand and contract. The urging means rotates the rotating body without supporting the weight, and the direction in which the urging means works is substantially perpendicular to the direction in which the gravity works, and is hardly affected by the gravity.
Patent Document 11 relates to a undulation gate, and the undulation gate includes a door body 4 provided with a water stop plate and a door body 21 that supports the door body 21, and the door body 21 is formed on a sliding surface provided on the door body 4. It is provided with “wheels that move along” and makes the door body 4 stand up or lie down. However, Patent Document 1
1 is perpendicular to the door body 21 when the door body 4 is standing upright and is parallel to the door body 21 when the door body 4 is lying down, so that the weight of the door body 4 is the axis of the door body 21 when the door body 4 is lying down. It is supported in the direction perpendicular to the axis, not in the axial direction. The rotation biasing means of the door body 21 supports the weight of the door body 4. Therefore, the urging force for raising the door body 4 when lying down increases.
Patent Document 12 relates to a moving device that supports a moving load on a rotating shaft of a “cam body with a plurality of wheels mounted on the outer edge and a spiral curve”, and an action line of a large force supported by the plurality of wheels is The cam body rotates near the rotation axis of the cam body with a small force, but the rotational force around the rotation axis shows the maximum value when two of the wheels touch the ground, and the maximum value when one of the wheels touches the ground. Decrease or increase from zero to zero. The maximum value increases as the magnitude of the rotational force acting around the rotation axis pulsates. In the case of the present application, since the number of stores is limited to one, the maximum value is reduced accordingly.
The present invention provides a “problem to ensure that the door rotates slowly and is securely and quietly sealed”.
However, as described above, an effective means is provided for the problem that the prior art has attempted to solve. Needless to say, the technology provided by the present invention can naturally be used in industrial fields other than doors.

JP2006-9547 JP 2005-273199 A JP-A-9-177425 JP 11-50734 A JP 2006-145068 A JP2007-177459A JP 2006-306359 A JP 62-59785 A Shokai 61-86732 JP-A-4-325314 JP2007-70924 JP 2006-306368

A “spring-driven door” rotates slowly when closing with a small force, but the door may stop in the middle of rotation. If it is sealed without stopping in the middle, a violent impact sound will be generated at the time of sealing. The “door closer with a hydraulic cylinder” rotates the door slowly so that no impact noise is generated when it is sealed. However, there is a “defect that the door feels heavy when the door is opened”.
The present invention has been made in order to provide a “door that does not feel heavy when opened” and a “spring-driven door” that does not emit a large impact sound when closed.
The spring has the property of expanding and contracting in an instant, but the spring with a small amount of expansion and contraction operates slowly, so the “spring-driven door” of the present invention operates slowly with insufficient force. It is what I did.
"A large impact sound when closing" is a force that is more than necessary when closing, and the extra force is converted into sound. To keep the secret in the room, "the force that the door presses against the door is static pressure The cause is that it acts as an impact load.
When the latch is recessed immediately before closing (hereinafter referred to as latch contact), the resistance of the latch, the rotational resistance around the pivot axis O, and the air resistance received by the door surface act on the door. The inertia force attached to the door (hereinafter referred to as the door inertia force) counters. The rotational resistance around the pivot axis O varies not only when the door is stationary and when it moves, but also varies depending on the door. Although different, in the present invention, the “force acting on the door” acts without excess or deficiency when the latch is recessed in any case or any door.

In order to remove the influence of the inertial force of the door when the latch is recessed, the present invention is brought close to a stop state so that a device for opening and closing the door (hereinafter referred to as an opening and closing device) continues to operate even when the door is stopped. In order to reduce the influence of the inertial force of the door, a large force is not applied to the door. By reducing the “force applied to the door”, the force required to open the door is reduced. The door does not feel heavy when opening the door.
The present invention is generally “simple technology that has not been adopted for doors” and has an unprecedented effect in the field of doors. Examples are shown in the examples. In addition, the present invention "reducing the impact sound when closing"
It is a matter of course that these means contribute to a plurality of other fields that are not related to the door.

In order to reduce the “impact sound when a door that is moved by a spring is closed”, it is necessary to solve a plurality of problems. The “part 1 of the problem” to be solved by the invention is “how to apply different magnitudes of force in the two ranges before and after the latch contact”.
Since the operation of indenting the latch involves the rotation of the door, the “force to indent the latch” is larger than the “force to simply rotate the door”. Rotate the door with as little force as possible so that the door that stops from anywhere in "(A) range" barely starts moving (hereinafter referred to as "(A) rotation" The rotation means in the “(I) range” is referred to as “(
")" Means of rotation. If the door is rotated with a large force so that it does not stop at the time of latch contact in the “(A) range”, the impact sound at the time of closing increases. Therefore, the magnitude of the “force acting on the door” at the time of latch contact does not switch from small to large (hereinafter, means for switching the magnitude of “force acting on the door” is referred to as “switching means”). Don't be.

The “part 2 of the problem” to be solved by the invention is “how to dent the latch while processing different door inertial forces depending on the closing opening degree”.
Even if the “force acting on the door” is kept small in the “(A) range”, the rotation speed of the door continues to increase as long as the force continues to act. It increases further when a large force is applied. When the door comes into close contact with the door stop, the kinetic energy possessed by the door is converted into an impact sound. Kinetic energy 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.
Even if the `` force to dent the latch when the door is stopped '' is large when the latch is in contact, the door is moving, but the door inertia force only slightly participates in the door sealing operation. Decrease “power”. When the speed of the door exceeds a certain value, the door is fully closed with only the inertial force of the door, even if there is no “force acting on the door”. The impact sound when the door is fully closed with just the inertia of the door is
The door speed becomes a non-negligible size just by increasing the constant value slightly.
If the door inertia force is eliminated at the time of latch contact and the door is sealed, or if the door is sealed while disappearing, the impact sound can be adjusted regardless of the door inertia force. In the present invention, the door inertia force is participated in the sealing operation without disappearing, and the door is sealed while converting the door inertia force into the sealing force. Reduce the required force.

The “part 3 of the problem” to be solved by the invention is “how to continue to operate the switchgear even when the door is stopped”.
Since the impact sound reacts sensitively to the door inertia force, it is necessary to keep the door inertia force as small as possible and stay within a certain range at the time of latch contact. In the “(A) range”, the “force acting on the door” "Is kept small to reduce acceleration, and" means for decelerating the door "is taken at the end of" (A) range "or at the beginning of" (A) range ".
At the time of latch contact, “(A) rotating means” causes the door to rotate and “open / close device to dent the latch”
There is no. If the door is sufficiently decelerated, the door stops due to the resistance of the latch. Since the opening / closing device does not have the force to rotate the door, it stops with the door when interlocking with the door. The door of the present invention is in a state where the door stops or closes to the stop state when the latch comes into contact, and the opening / closing device does not interlock with the door or slightly interlocks without rotating the door or with a small force of the opening / closing device. While the door is slightly rotated, a force is provided to dent the latch after the latch contact.

At the end of the door rotation, the maximum force to dent the latch is required, but the spring force is attenuated and minimized. The “part 4 of the problem” to be solved by the invention is “how to seal the door with a small force of a spring”.
Although "the greatest force in the fully opened point range of the door" is required, "the force of recessing the latch" door from the time of the latch abutment in order to previously recessed latch male portion of the door the door presses the doorstop If it continues to act until the door stop is pressed, the door is accelerated even in a range where the amount of rotation of the door is small, and an impact sound is generated. After the latch is recessed, little force is required until the latch pops out again and fits into the door frame W. It is desirable that the “maximum force in the full opening range of the door” be minimized when the latch is in contact.
The present invention has not allowed to act on the door more than necessary force of the spring so that it does not accelerate even "range of (ii)," but "the range of (A)", do not use a strong force of the spring. Instead of reducing the force of the strong spring, the force of the weak spring is expanded and applied to the door. Therefore, it is important to control the “force acting on the door” at the time of sealing.

Doors vary in size and weight, and there is a limit to how a single switchgear can be adapted to any door and always have the same effect and operate as desired. The braking force changes according to the magnitude of the force, and the applicable range is expanded by changing the structure of the switchgear. Further, in order to solve the above-described problems, a plurality of means described below are taken, but the plurality of means make up for insufficient effects.

“Means 1” to Solve “Problem 1” to “Problem 4” that the Invention is to Solve
As explained at the beginning of “Mode for Carrying Out the Invention”
"Rotating body consisting of two links D and W" and "rotating part consisting of one or more links" and "rotating part consisting of one or more links" that rotate relative to each other by sharing the rotation axis O, provided on each of the two links D and W Mounting axis C
, Sw is a link device in which both ends of the expansion / contraction part are connected, and the opening / closing body is opened / closed by changing the distance between the attachment shafts C, Sw. There is a releasable restraining means for restraining the rotation around the shaft, and the releasable restraining means restrains the rotation of any of the connecting shafts or releases the restraint at a predetermined opening degree of the opening / closing body. do it,
An opening / closing device in which an action point of a force acting on the opening / closing body is transferred.

When the opening / closing device 1 is a “link device in which any adjacent link is connected by a sliding pair” as in the embodiment of FIGS. 1 to 7, for example, in FIG. W
, A has a sliding surface K on one link W, and a wheel B mounted on the other link A is connected to the sliding surface K.
The sliding surface K is provided with “the passage of the wheel B far from the rotation center O of one link W or the vicinity thereof”, and one side when the wheel B moves along the sliding surface K. This is characterized in that the link W of the link W is not or hardly accompanied by rotation. For example, in FIGS. 1 to 7, the door D moves with little or no rotation. The wheel B presses the sliding surface K and contacts b
, The pressing force Fb acts, the wheel B moves away from the vicinity of the center O of rotation, and the action line of the pressing force Fb also moves away, and the rotational moment acting on the center O of rotation increases.

In “range (a)”, the wheel B is restrained in the vicinity of the rotation center O, the rotation moment acting on the rotation center O is small, the rotation of the door D is large, and the rotation of the link A is small. In the “range (i)”, the wheel B is far away from the vicinity of the center of rotation O, the rotational moment acting on the center of rotation O is large, the rotation of the door D is small, and the rotation of the link A is large. When the action line of the pressing force Fb crosses the axial center line Za of the link A in the “switching range”, the rotation direction of the link A is switched and the restraint of the wheel B is released. The “switching means” is characterized in that the door D does not rotate at all or hardly, and the expansion / contraction part moves greatly without rotating the door or slightly, and the expansion / contraction part moves even if the door stops. to continue.
1 to 7 are examples in which the sliding surface K is provided on the door D or the door frame W, and the attachment part of the opening / closing part and the expansion / contraction part is a sliding pair. FIG. 17 and FIG. an embodiment of the kinematic pair,
If any of the connecting shafts is a slip pair, the same operation and effect can be expected. In addition, when the leaf spring is used in FIG. 30, the same operation and effect can be expected.

When the opening / closing device 1 is a “link device in which any adjacent link is connected by turning pair” as in the embodiment of FIG. 19, for example, in FIG. 19, “any one adjacent link” AA has a pressing force Fb by G1 and G2 provided on the other link D or W.
Oscillates between a position where the action line is held in the vicinity of the pivot O and restrained and a restraint release position where the action line of the pressing force Fb is away from the vicinity of the pivot O.
1 to 7 and FIG. 17 As in the case where the connecting shaft of FIG. 18 is a slip pair, the connecting shaft PP is constrained in the vicinity of the center of rotation O in the “range (A)” and acts on the center of rotation O. The rotation moment is small, the rotation of the door D is large, and the rotation of the link A is small. In the “range (ii)”, the connecting shaft PP is far from the vicinity of the rotation center O, the rotation moment acting on the rotation center O is large, the rotation of the door D is small, and the rotation of the link A is large. In the “switching range”, when the axial line Za of the link A, that is, the line of force action, crosses the axial line Zaa of the link AA, the rotation direction of the link A is switched and the constraint of the connecting shaft PP is released.

The opening / closing device No. 1 “characterized by restricting or releasing the rotation around any of the above-mentioned connecting shafts” is constrained to rotate at any of the connecting shafts and is connected with the connecting shaft in the middle. This means that the adjacent links become relatively integrated, and the adjacent links can be rotated by releasing the constraint. The fact that adjacent links are relatively integrated means that the number of links and the degree of freedom of the link device are one.
It is to reduce.
FIG. 9 shows an opening / closing device 1-1 in which any one of the “opening / closing device 1 /“ extensible / contracting portion including one or more links ”” is a spring. Is a four-joint rotation mechanism consisting of four links D, W, A, and V. When the adjacent links D and A are relatively integrated, the number of links of the link device is reduced by one,
I can't exercise. Movement can be achieved by using one of the links as a spring.

FIG. 9 is a diagram in which the link A in FIG.
When Zv, that is, the line of force action crosses the axis A Za of the link A, the rotation direction of the link A is switched and the constraint of the connecting shaft PP is released. The “spring spring V and link AA” of the urging means shown in FIG.
The same applies to the “continuum in which the two are connected by the connecting shaft Sa”.
FIG. 9 is an embodiment in which the attachment portion of the opening / closing portion and the expansion / contraction portion is a rotating pair, and FIG. 27 is an embodiment in which the other connecting shaft is a rotating pair. Then, the same operation and effect can be expected.
FIG. 27 shows a 5-joint rotation mechanism, which can move even if adjacent links J and A are relatively integrated, and the structure of the link device changes. In a state where the PP is not restrained away from the vicinity of the rotating shaft Sw of the rotating body J, the rotating force acting around the rotating shaft Sw is converted into a force pulling the door, and the rotation of the door D is small and the rotating body J rotates. Is big. "(I)
In this range, the connecting shaft PP is constrained in the vicinity of the rotating shaft Sw of the rotating body J, and the rotational force acting around the rotating shaft Sw is largely converted to a force pulling the door, and the rotation of the door D is small and the rotating body is rotated. The rotation of J is large. In the “switching range”, the link A and the rotating body J are relatively integrated with each other, whereby the revolution radius of the connecting shaft PP is restricted to be small.

The rotation mechanism of FIG. 4 includes releasable restraining means for restraining the rotation of the sliding surface K around the rotation axis O,
An opening / closing device 1 for releasing the restraint of rotation around the rotation axis O with the door opening when the curvature of the sliding surface K changes as a boundary, and the action of the pressing force Fb in the “range (A)” The line is constrained in the vicinity of the rotation axis C of the link A, the rotational force acting around the rotation axis C is small, the rotation of the link A is large, and the rotation of the sliding surface K is small. The action line of the pressing force Fb is the rotation axis C of the link A in the “range (ii)”.
The constraint force is released away from the vicinity of the shaft, the rotational force acting around the rotation axis C is large, the rotation of the link A is small, and the rotation of the sliding surface K is large. In the “switching range”, the sliding surface K rotates largely with little rotation of the link A.
The rotation mechanism of FIGS. 22 to 24 is also an opening / closing device 1 like FIG. 4, and includes a releasable restraining means for restraining the rotation around the connecting shaft P, and the shaft core line Za of the link A and the rotating body J The rotation around the rotation axis O is released or restricted with respect to the opening of the door when the shaft core line Zj is arranged in a straight line. In the “range (a)”, the line of action of the pressing force Fb is constrained in the vicinity of the pivot axis O, the rotational force acting around the rotation axis C is small, the rotation of the door D is large, and the rotation of the link A is small. In the “range (ii)”, the line of action of the pressing force Fb is released from the vicinity of the rotation axis C of the link A, the constraint force is released, the rotational force acting around the rotation axis C is large, the rotation of the door D is small, and the link The rotation of A is large. In the “switching range”, the link A rotates largely with little rotation with the door D.

The opening / closing device 1 is “an opening / closing device 1-2 in which the opening degree of the opening / closing member that restricts or releases the rotation of any of the connecting shafts varies depending on the rotation direction of the opening / closing member”.
In the opening / closing device 1, the opening of the door when the action line of the pressing force Fb moves away from the vicinity of the rotation axis C in the process of closing the door is the opening of the door, and the action line of the pressing force Fb is the rotation axis in the process of opening the door. There is a feature that is smaller than the opening of the door when returning to the vicinity of C, and the rotation range immediately before closing and before the latch contact is "(A) rotating means" in the closing process, but open the door and hold your hand When releasing, the rotation range before the latch contact is operated by “(i) rotation means”, and even if resistance is provided in this range, the door is fully closed without stopping. Even if the door is stopped by applying resistance just before the latch contact just before closing, the door inertia force will cause the latch to dent by rotating only with the door inertia force with the "force acting on the door" being zero. Even if the “force” is made small, the door does not remain stopped wherever the door opens and is released.
In this way, the switchgear 1 solves “the problem 1” to “the problem 4”.

Further, the opening / closing device 1 is “a rotation mechanism in which a rotating body rotates by a force F around a rotation axis, and a rotation force M acting around the rotation axis, a rotation axis, and an action line of the force. The relationship established between the distance L and the distance (M =
F × L), a rotation control mechanism that changes the magnitude of the rotational force M or the force F by changing the magnitude of the distance L,
“(A) rotating means” for rotating the rotating body with a small force, “(I) rotating means” for rotating the rotating body with a large force, and “(A) rotating means” to “above” (I) rotating means ”or“ switching means ”for switching from the“ (ii) rotating means ”to the“ (a) rotating means ”, wherein the“ switching means ” Opening / closing device 2 having a rotation control mechanism, characterized in that the distance L is switched from small to large or from large to small with little or no rotation of the rotating body at the opening degree. " But there is.

“Opening / closing device 2” is the “distance between the force action line and the rotation axis” by the movement or transition of the force action point or by the rotation of the force action line (hereinafter referred to as “the distance between the force action line and the rotation axis” The distance L) changes, and the forms in which the distance L changes include the following switching devices 1-1 to 7.
The opening / closing device 2-1 is an opening / closing device described in the opening / closing device 2 including a rotation mechanism in which the direction of the force F acting around the rotation shaft is switched from the radial direction of rotation of the rotating body to the circumferential direction. The action line of the force Fb rotates. For example, in FIG. 1 to FIG. 9, the action line direction of the force F acting around the pivot O in the “range (A)” is directed toward the pivot O and “around the pivot O”. The distance L between the action line direction of the working force F and the pivot axis O (hereinafter, the distance between the action line of the force F having a certain magnitude and the rotation axis is called the action force distance Lo) is small. The rotational force Mo acting around is small, deviating from the direction of the pivot axis O in the “(range)”, and the acting force distance Lo turns large.

Opening / closing device No. 2-2 is described in Opening / closing device No. 2 including a rotating mechanism in which the point of action of the force F acting around the rotating shaft moves along a “passage continuing from a position close to the rotating shaft to a position far from the rotating shaft”. Opening and closing device. For example, FIGS. 1 to 3 include a “passage of the wheel B continuing from a position Ko close to the rotation axis O to a position Ke far away”. The same applies to FIGS.
In FIG. 8, the attachment shaft Sa of the tension spring V at a position close to the rotation axis O moves along a “circular orbit continuous from a position near the rotation axis O to a position far from the rotation axis O”. The switchgears 2-1 and 2 have the action point "
It is stopped at a position close to the rotation axis of the rotating body in “range (a)” and moved to a far position in “range (ii)”.

In the opening / closing device 2-3, the action point of the "(a) rotating means" is a position close to the rotation axis,
The switchgear described in the second switchgear having a rotation mechanism in which the action point of “(i) rotating means” is a distant position. The action line of the force F is transferred, and for example, the force of the spring V acts at a position close to the pivot axis O in “range (A)” in FIG. 9. The rotating body A at a position far from the pivot axis O rotates in the “range (ii)”, and the wheel B presses the sliding surface K. In the “switching range”, the rotating device V that operates at a position close to the rotating shaft is switched to the sealing device B that operates at a position far from the rotating shaft. The same applies to FIGS.

As shown in FIG. 4, the opening / closing device 2-4 is “a rotating device in which rotating bodies separated from each other around a pair of rotating shafts rotate relatively, and one rotating shaft rotates around one rotating shaft. The rotating body includes a sliding surface, and the other rotating body that rotates about the other rotating shaft has a wheel mounted at a tip, and the wheel is pressed against the wheel or the wheel is the sliding surface. The sliding surface relatively moves along the wheel while pressing the wheel, and the shape of the sliding surface is such that when the wheel is in the middle of the sliding surface, the wheel slides. The action line of the force that presses the surface has a small distance between one of the rotating shaft and the other rotating shaft, and the wheel presses the sliding surface when the wheel is at the end of the sliding surface. The line of action of the force is a switching device in which the distance between the one rotating shaft and the other rotating shaft is a large curve. Switchgear described Part. "
4 (a) and 38 (b), the distance to the other rotating shaft is changed, and in FIGS. 38 (c) and 38 (d), the distance to one rotating shaft is changed. 38 (c) and 38 (d) are involute vortex lines. FIG.
In the case of FIGS. 38 (a) and 38 (b), the rotation axis of “link A for attaching wheel B to the tip” and FIG.
c) In the case of (d), the rotation axis of the sliding surface of the involute vortex line and the line of action of the pressing force Fb keep a constant distance.

Unlike the switchgears 2-1 to 2-3, when the door is closed, the wheel B moves along the sliding surface K from a position far from the rotation axis to a position close to the rotation axis. In the case of FIGS. 38 (a) and 38 (b), when the sliding surface rotates with a constant rotational force, the force for pressing the wheel is the rotational axis of the wheel on one side (rotating body having the sliding surface). The pressure increases and the other (rotating body to which the wheel is attached)
The distance L between the rotary shaft and the rotary shaft is constrained to be small, and the working rotational force is kept small around the rotary shaft of the other side (the rotating body on which the wheel is mounted). When the wheel is in a position close to the one side (rotating body having a sliding surface) rotating shaft and the distance L between the pressing force and the rotating shaft turns large, the other side (rotating body to which the wheel is mounted) The working force increases with the lever principle.

The switchgear 2-4 has a form in which the action point of the force F does not move in the “switching range” and the action line of the force F rotates, and FIG. 38 is also shown in FIGS. In the case of (c) and (d), the action line of the force with which the wheel presses the sliding surface when the wheel is in the middle of the sliding surface in “range (A)” is “attaching the wheel B to the tip. The acting force distance Lo between the rotating shaft of the “link A” or the “rotating shaft of the sliding surface of the involute vortex line” is small, and the rotating force acting around the rotating shaft is small. When the wheel is at the end of the sliding surface, the action line of the pressing force Fb rotates in the “switching range” and the action surface distance Lo increases in the “(range)” range. Therefore, the rotational force acting around the rotation axis is large.
In the “(A) range”, the wheel B moves greatly on the sliding surface K and the movement is reduced by the “(i) rotating means”, but the sliding surface K is small in the “(A) range”. Rotate and rotate significantly in the “switching range”. The rotation mechanism of this switchgear is in a direction (hereinafter referred to as a radial direction) toward the center of rotation of “link A for attaching wheel B to the tip” or “cam body having sliding surface of involute vortex line”. It is a rotating mechanism characterized in that a large force acts and moves with a weak force in a direction perpendicular to it (hereinafter referred to as a circumferential direction).

The switchgears 2-1 to 4 are those in which the “force acting on the door” is proportional to the acting force distance Lo. For example, when the same force F acts on the door in FIG. It is easy to move and it is difficult to move at close positions. In the relational expression (W = FXL), when the action point of the force is close to the pivot axis O, the rotational force Mo acting around the pivot axis O is small, and the force acts weakly on the rotating body. The action point of the force is the pivot axis. When it is at a position far from O, the rotational force Mo acting around the pivot axis O is large and the force acts strongly on the rotating body.
The “force acting on the door” is inversely proportional to the distance L (hereinafter, the distance between the rotation axis at which a constant rotational force acts and the force acting line is referred to as the driving force distance Lv). It is recognized also in 1-4.

For example, in FIG. 1 and FIG. 11, the opening / closing device 2-5 has a small force at a position far from the rotation axis and a large force at a near position. In the following open / close devices 2-5 to 7, the "force F acting on the door" is inversely proportional to the distance L, and the radius of rotation of the line of action of the force changes. The magnitude of the force F acting on the door is increased to increase the rotational force M that rotates the door.

The opening / closing device 2-6 is, for example, as shown in FIG. 27, a “link device that connects two expansion / contraction portions to two attachment shafts provided on each of two opening / closing bodies”. The two adjacent links in the section are disengaged from each other, and the two links that are engaged and adjacent to each other rotate relatively. The two links become relatively integrated. At this time, the distance from the center of rotation to the line of action of the force F becomes smaller than the previous driving force distance Lv, and the rotational force acting around the center of rotation is largely converted to the force F.
The link device of FIG. 27 is a 5-joint rotation mechanism, and operates as a 4-joint rotation mechanism when the two links are engaged and become relatively integrated, and the two links are separated and become straight. The two links operate by pushing with one link, and operate as a four-bar rotation mechanism with different forms.

The opening / closing device 2-7 is, for example, as shown in FIGS. 22 to 24, “a link device for connecting an expansion / contraction portion composed of two links to two mounting shafts provided on each of two opening / closing bodies”. “(A) Rotating means” which moves in a state where the shaft cores of the two links are not arranged in a straight line and the above 2
“(I) Rotating means” that moves in a state where the axial cores of the two links are arranged in a substantially straight line, and a state in which the axial cores of the two links are arranged from a state in which they are not arranged in a straight line, or in a straight line "Switching means" to switch from the state arranged to the state not arranged,
An opening / closing device characterized in that the axial lines of the two links are arranged in a straight line, and the magnitude of the force acting on the axial lines of the two links is increased. In the case of the embodiment of FIGS. 22 and 23, the shaft cores of the two links extend straight from the folded state. In the case of the embodiment shown in FIG. 24, the shaft cores of the two links are folded from a state where they extend in a straight line. In this case, the axis lines of the two links overlap.
The urging means of this link device is provided around “a connection shaft whose rotation direction does not reverse in the middle of any connection shaft of the link device”, but even if it is provided on any of the connection shafts, When the axial line turns into a straight line, the magnitude of the force acting on the axial line of the two links increases.

Whether controlling the "magnitude of the force acting on the door" using a resistor or by means of changing the "distance between the rotation axis and the force acting line", the "force acting on the door" If the time variation of “size” is the same, the door operation is the same.
Even when rotating work and sealing work are processed by a series of operations of one device, there are separate devices engaged in the rotating work and the sealing work, and each device “force acting on the door” in two different rotation ranges. Are different in size and change in the "switching range", the magnitude of the "force acting on the door" is controlled by the change in the "distance between the rotation axis and the force action line" Even if you do not
The temporal change in the “magnitude of the force acting on the door” results in the same door operation.
“Means 2” to Solve “Problem 1” to “Problem 4” that the Invention is to Solve
30 to 32, there are a rotation device that transmits rotation to the door only in “(A) rotation range” and a sealing device that transmits rotation to the door only in “(I) rotation range”. A switchgear No. 3 characterized in that a spring that operates in the “(A) range” and a spring that operates in the “(A) range” alternate in the “switching range”. "

Each spring is “a biasing means that is valid until halfway and becomes invalid from the middle” and “a biasing means that is invalid until halfway and becomes valid from the middle”. In FIG. The force of the spring works ineffectively, and the spring expands and contracts so that it works effectively. In FIG. 32, the wheel B is not engaged with the sliding surface K, “the spring force is ineffective, and the engagement is made effective. Each operates independently without being influenced by the other.” When the door and the drive unit are not interlocked in the “switching range”, the movement of the “switching unit” is constant, and the time required for the latch male part Rd to come into contact with the female part Rw and begin to dent is constant. Since the door rotates only with the door inertia force, the amount of rotation of the door within the required time greatly varies depending on the magnitude of the door inertia force. FIG. 32 shows an opening / closing device that determines whether or not the door is suddenly stopped by the “amount that the door rotates only by the inertial force of the door”.

"Means part 3" to solve "part 1 of problem" to "part 4 of problem" to be solved by the invention
As shown in FIG. 8 and FIG.
"Rotating body consisting of two links and D and W", which share the rotation axis O and rotate relatively, and 2 above
A link device in which both ends of an “extensible / contracting portion composed of one or more links” are connected to mounting shafts C and Sw provided on each of the links D and W, and the mounting shafts C and Sw follow a predetermined path. The mounting shafts C and Sw can be moved by a spring that can be set to a predetermined value from zero to infinity. Opening and closing device 4 which is biased so as to return to the “initial position when it is a natural length”. "

In FIG. 1, the contact point b between the wheel B and the sliding surface K is also a movable mounting shaft, and the predetermined passage is a curved track of the sliding surface K moving away from the pivot O. Depending on the curved track, the door may rotate. The wheel B can move along the sliding surface K without accompanying. The door and the telescopic part do not interlock, and the telescopic part continues to move even if the door stops. 2, the curved track of the sliding surface K rotates and is urged by the push spring U. In this case, the linkage between the door and the extendable part can be freely designed as compared with the case of FIG.
8A to 8D, the spring support shaft Sa is also a movable mounting shaft, and the predetermined passage is a circular orbit about the connection shaft C. Thus, the opening / closing device No. 1 is the opening / closing device No. 4 in which the door and the expansion / contraction part do not interlock and the expansion / contraction part continues to move even when the door stops. The switchgear 4 only limits the releasable restraining means to the mounting shaft.
In FIG. 28, an elastically deformable leaf spring for the link A is provided with a releasable restraining means for restraining rotation around the connecting shaft other than the mounting shaft, and is an upper opening / closing device No. 1, but the door and the telescopic portion When the door is stopped without interlocking, the expansion / contraction part continues to move, and at the time of sealing, even if the movement of the expansion / contraction part stops, it can be sealed by the force of the leaf spring.

1 and 8, adding the link of the rotating body Jc increases the degree of freedom of the link device and makes the operation unstable. However, when the movable mounting shaft is at the start of the passage and at the end of the passage It operates as a different type of link device.
In FIG. 1, FIG. 22 and FIG. 22, the connecting shaft C revolving around the connecting shaft Cj is a movable mounting shaft, and the predetermined passage is circularly activated. The “spring that can be set to a predetermined value from zero to infinity in rigidity” is the push spring U. When the stiffness of the spring is set to infinity, the mounting shaft is fixed, the door and the telescopic part work together, and when the stiffness of the spring is set to zero, the mounting shaft is not fixed and can move freely Thus, the door and the telescopic part do not interlock, and the telescopic part continues to rotate independently without rotating the door. Even if the door stops at the time of latch contact, the telescopic part continues to move. On the contrary, the door can move even if the expansion / contraction part stops, and the door is sealed not by the driving force Mv of the expansion / contraction part but by the force of the push spring U as described with reference to FIGS. As illustrated in FIG. 10, when the rigidity of the spring is set to be small, the expansion / contraction part provides a rotational force little by little to the door while greatly expanding / contracting the spring. The expansion / contraction part provides the door, but even if it is large, it can be limited by setting the upper limit of the expansion / contraction of the spring.

In the process from just before closing to the time of sealing, the force acting on the door is the driving force Mv of the telescopic part and the inertia force of the door that is "the force that works in the direction of closing the door" and "the force in the opposite direction" around the pivot axis O Rotation resistance, air resistance, and latch resistance work, but the "switching means" is the door when no force is applied to the door with the "force acting in the direction of closing the door" set to "force in the opposite direction" or less. Regardless of the operation, the door is sealed. When the door is closed by the door inertia force regardless of the “switching means”, an impact sound is generated, which must be prevented.
It is good to apply a force in the opposite direction to the door inertia force, but when the force in the opposite direction is constant, for example, when a certain resistance acts, the door is stopped by the closing start opening degree. And resistance may not work at all. The present invention provides a sealing device that seals while receiving resistance without stopping the door. For example, FIG. 6 and FIG. 7 show a closing device that does not stop halfway. It moves along the door frame W simultaneously, receives a force for closing the door from the wheel B, and receives a force in the opposite direction from the door frame W. The latter is a resistance according to the magnitude of the door inertia force, which is neither too effective nor at all. The wheel B is connected to the connecting shaft Cj.
Sealing is prevented until it passes over.

The “means 4” for solving the “problem 2” to be solved by the invention is provided in each of the “opening / closing body comprising two links and D and W” and the two links D and W. Mounting shaft C, S
It is a link device in which both ends of the “extensible part composed of one or more links” are connected to w, and the force acting on the door on the mounting shafts C and Sw and the force in the opposite direction, that is, the rotation of the opening / closing body The opening / closing apparatus 5 characterized in that the force to prevent the rotation of the opening / closing body acts simultaneously. "
In FIG. 8, two wheels are attached to the “attachment shaft C of the opening / closing body and the expansion / contraction part”, and a sealing force and a blocking force simultaneously act on each of them. The force that prevents sealing does not work when the door inertia force is negligible, and stops the door when it is large. When time passes and the door inertia disappears, the door starts moving again. FIGS. 12 to 14 show an embodiment in which the magnitude of the braking force increases with the magnitude of the door inertia force.

The “means 4” for solving the “problem 4” to be solved by the invention is “a rotating device in which rotating bodies separated from each other around a pair of rotating shafts rotate relatively, One rotating body that rotates about the shaft has a sliding surface, and the other rotating body that rotates about the other rotating shaft has a wheel mounted at the tip, while the sliding surface presses the wheel. Or the rotating device in which the sliding surface moves relatively along the wheel while the wheel presses the sliding surface,
The shape of the sliding surface is such that the line of action of the force with which the wheel presses the sliding surface is such that the distance between the one rotating shaft and the other rotating shaft is kept small or large. Device 5 "
4 (a) and 38 (b), the rotation axis of “link A with wheel B attached to the tip” and FIG.
In the case of 8 (c) and (d), the rotation axis of the sliding surface of the involute vortex line and the line of action of the pressing force Fb keep a constant distance. In each case, the axial line passing through the “contact point b between the wheel B and the sliding surface K” and the rotating shaft and the action line of “the force Fb that the wheel B presses the sliding surface K” are close to each other. 4 and 38, when the distance is kept small, a small force acts in the circumferential direction, a large force acts in the radial direction, and the radial force is supported by a rigid body. . The door is sealed by a large force acting in the radial direction with a small circumferential force.
When the axial cores of the two adjacent links described above are arranged in a straight line, the force acting on the connecting shaft of the two links acts on the axial core of the link, and a small force is generated in the circumferential direction of the circular orbit of the connecting shaft P. This is the same as the action of a large force in the radial direction.
Further, as described in FIGS. 35D and 35E, when the distance is kept large, a large force acts in the circumferential direction and a small force acts in the radial direction. Even if the spring is strong like an accelerator pedal, the stepping force is small.
If the “rotating device in which rotating bodies separated from each other rotate relative to each other” is changed, the positions of one rotating body and the other rotating body are switched, and the position of the acting force is also switched. As shown in FIG. 4 and FIG. 29, for a door whose rotation axis is vertical, a strong force is applied to the door while preserving a strong force in “range (A)”. 39. As will be described with reference to FIG. 40, the lid is moved up and down with a small force while supporting the weight of the lid with the axis of the rigid body even with respect to the lid having a horizontal rotation axis. It is effective as both rotating means and moving means.

Since the “switching means” of the present invention operates without rotating the door, there is a drawback of ending the operation in an instant in an unloaded state. It is desirable to install and seal the door. Further, since the operation is larger than the operation of the opening / closing unit, the delay unit does not need to be strong if the delay unit operates on the driving unit instead of acting on the opening / closing unit. The switchgear shown in FIG. 37 is “a switchgear provided with means for decelerating the rotation around the connecting shaft other than the pivot O in the link device of the switchgear”. In general, the collision phenomenon is a phenomenon that suddenly stops at the end of movement, but the door D in FIG.

The force required to open the door is a force having the same magnitude and opposite direction as the “force acting on the door during the door closing process”. The force required to open the closed door is a force having the same magnitude and the opposite direction as the “force acting on the door during the process of sealing the door”. Therefore, a door that is closed by applying a small force to the door can be opened with a small force even when it is opened, and a door that presses the door stop with a strong force requires a large force when it is opened. The conventional latch moves parallel to the door surface by “a force acting on the door surface in a direction perpendicular to the door surface”, and moves by a part of a large force. It was necessary to set it large.
Therefore, even if the door feels light after the door is opened, it receives a “feeling that the door is caught by something” at the beginning of opening.
The embodiment of FIG. 33 reduces the resistance of the latch by rotating the latch.
)) "Rotating means" can be set small, "door closer with hydraulic cylinder"
The "defects that feel heavy when opening the door can be eliminated."
The embodiment of FIG. 33 is a locking rotating body Ge that is rotatably supported on a rotating support shaft Ig provided on one side of “the side surface of the door opposite to the door pivot” and “the side surface of the door frame facing it”. And a locking sliding surface Kf provided on the other side, and the rotation support shaft Ig is moved while the locking rotating body Ge moves along the locking sliding surface Kf by rotation of the door in the closing / opening direction. A latch device characterized in that the force that rotates around the shaft and prevents the door from rotating in the opening direction is supported by the rotating support shaft Ig or the outer edge Re of the locking rotator. The line of action of the force is a straight line passing through the contact b between the locking rotator Ge and the locking sliding surface Kf and the rotation support shaft Ig, and is also the axis of the locking rotator Ge. The circular motion of the contact b is “the rotation mechanism of the present invention that supports a strong force in the radial direction and moves with a weak force in the circumferential direction”.

In the link mechanism of the present invention, the acting line of the force sharing the intersection and the axial line Za of the link A cross the axial line Za of the link A such that the acting line of the force acting on the intersecting point crosses the axial line Za of the link A. It is based on a rotating mechanism that rotates in reverse, and can be kept stationary by utilizing the change in the biasing direction of the door rotation when the door is fully open. In this case, the “opening degree of the door in which the urging direction is reversed” is limited to the vicinity of the fully open position, and if the “opening degree of the door in which the urging direction is reversed” is slightly pushed in the closing direction, the door is closed arbitrarily.
In the embodiment of FIG. 34, “the opening degree of the door whose urging direction is reversed” is provided at two positions of the fully open position and the fully closed position. When the door that is stationary in the fully closed position is pushed in the direction of opening a little, the door opens freely and reaches the fully open position.
“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 A door 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 structure oscillates between a fully closed direction biasing position Ga1 that is stationary when the door is biased in the fully closed direction and a fully open direction biasing position Ga2 that is stationary when the door is fully biased in the fully open direction. Shiggle spring V
The swinging body A biased by V and the swinging body A from the fully closed direction biased position Ga1 to the fully open direction biased position G1
A door provided with the opening direction switching means J1 for switching to a2 and the closing direction switching means J2 for switching the rocking body A from the fully open direction biasing position Ga2 to the fully closed direction biasing position Ga1. "

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 the door closer of the present invention, the door is not felt heavy when the door is opened so that the difference between the case where the door closer is attached and the case where the door closer is not felt is felt.

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 should be attached to an indoor door frame that does not have the strength to support the force of the strong spring. I can't.
Since the door closer of the present invention moves with a weak spring, it can be attached to a weak frame such as an indoor wooden door frame. The frame of the mounting part will not be broken and the mounting bolt will not come off.
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.

In terms of performance, it is excellent in that it has little deterioration in performance due to wear, has few failures, and has a long life. It is inexpensive because the number of parts is small and the strength of the material is not required, and the operating range does not protrude from the door surface. It is also excellent in that it can be stored in the device or in a small case because it is within a narrow circle in the elongated area or near the pivot of the door.
When the door drive unit of the present invention is moved by an electric motor, the rotation speed of the door can be made constant, and in the range from immediately before closing to the time of closing, the door requires time for large rotation of the drive unit. Rotate small. The closing device of the present invention has better performance when it is moved by a 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 moved by a motor.

The rotating mechanism for rotating the door of the present invention has a feature that a large force works at the end of rotation, and a small force is applied before that. There is a characteristic that the rotational force is large and the resistance is different between the opening direction and the closing direction, and a characteristic that operates with a small force while supporting a large force. As shown in the drawings, it can be used as a technique for moving the joint of the robot, as a shock absorber, or as a transport device. Thus, the rotation mechanism of the present invention is not limited to doors and can be applied to other industrial fields.

Operation explanatory diagram of the switchgear provided with the mounting shaft of the sliding pair Operation explanatory diagram of the switchgear in which the wheel presses the sliding surface Operation explanatory diagram of the switchgear in which the wheel pulls the sliding surface Operation explanatory diagram of the rotating mechanism where the wheel moves along the sliding surface Operation explanatory diagram of the sealing device in which the wheel reciprocates Operation explanatory diagram of a sealing device having a sealing sliding surface and a sealing blocking sliding surface Operational explanation of sealing device with sliding surface rotating Operation explanatory diagram of the switchgear in which one of the links is a spring Operation explanatory diagram of switchgear where action point is transferred Operation explanatory drawing of the sealing device sealed through the first door Operation explanatory diagram of a driving rotating body provided with a sealing wheel and a rotating wheel Operation explanatory diagram of the opening and closing device that separates the spring of the sealing device and the rotating device Operation explanatory diagram of the speed reducer that converts inertial force into braking force Operation explanatory diagram of the sealing device where the sliding surface presses the wheel Operation explanatory diagram of the switchgear provided with the direct acting urging means Operation explanatory diagram of sealing device with sliding surface perpendicular to door surface Operation explanatory diagram of a driving rotating body provided with "switching means" Operation explanatory diagram of the deceleration means that operates at the start Operation explanatory diagram of the restraint releasing means where the axis of the link crosses the rotation axis Illustration of the operation of the link device connected with a slip pair other than the mounting shaft Action diagram of the door that is sealed with the force to stop the rotation of the door working Operation explanatory diagram of the sealing mechanism in which force acts on the maximum value at the time of latch contact Explanatory drawing of the effect that the axial center line of two links become a straight line Explanatory diagram of the effect of the link axis and the force action line overlapping Operation explanatory diagram of the sealing force control device after the latch is recessed Operation explanatory diagram of the finger padding prevention device Operation explanatory diagram of the rotation mechanism in which the two links engage and disengage Operation explanatory diagram of sealing device with link as leaf spring Operation explanatory diagram of sealing device with multiple operations Operation explanatory diagram of a rotary urging device including switching means Operation explanatory diagram of the linear motion type urging device provided with the switching means Operation explanatory diagram of the door sudden stop device that runs idle at the time of relay Operation explanatory diagram of latch device Operation explanatory diagram of the door that opens fully when it opens a little and closes when it closes a little Operation diagram of hybrid shoes Operational diagram of robot's finger joint Operation explanatory diagram of shock absorber Involute vortex line drawing example Cam body moving device whose outer edge is an involute vortex Implementation of a device to support the standing fall of the lid

The opening / closing device of the present invention shown in each embodiment includes an opening / closing body and an expansion / contraction section (or drive section), and the opening / closing body has two links D and W that rotate relative to each other by sharing a rotation axis O, and one is a door. D and the other door frame W
And the both ends of an expansion-contraction part are connected to the attachment axis | shaft C and Sw (connection axis | shaft C, fixed spindle Sw) provided in each. The link device includes two links D and W constituting the opening / closing body and a plurality of links constituting the expansion / contraction part, and the opening / closing body opens and closes when the distance between the attachment shafts at both ends of the expansion / contraction part changes. A driving force Mv acting in the direction of arrow A in the figure around any of the connecting shafts, or an axial force or bending force acting on any of the links transmits the rotational force Mo around the pivot axis O. When the door frame W is fixed, the door D rotates in the direction of arrow B in the figure.
When the telescopic part is a single link with no change in length, the link device is a non-deformable triangle and does not move. When two adjacent links are connected at the opposite corner, they can move. Or, if one of the links is a “spring or jack of varying length”, it can move. For example, FIG.
Is a link device composed of three links, and constitutes a triangular link device. The link device is movable by connecting the opening / closing body and the expansion / contraction portion at the opposite corners.
When the expansion / contraction part is composed of two or more links, the link device is a deformable polygon and moves. When the expansion / contraction part is two links, the distance between the mounting shafts at both ends of the expansion / contraction part changes as one of the links rotates, and the length of one of the links changes in the triangular link device described above. It becomes the same as the device to do.

“The link device with three links and one of the connecting shafts is a sliding pair” is provided with a “path through which the connecting shaft can reciprocate” in one link of the link device, and the length of the one link changes. This is the same as the “link device in which one of the three links is a spring” in that the triangle is deformed, and all the four-joint rotation mechanisms in which the spring is changed to two links are also on one side of the triangle. It is a link device that moves by changing its length. Since adjacent links rotate around one of the connecting shafts, two adjacent sides sharing one of the connecting shafts are opening / closing bodies, and the remaining one side is an expansion / contraction part. Including the four-bar rotation mechanism, this is a “deformable triangular link device”.

When two adjacent links making up a link device composed of four or more links come into contact with each other and become relatively integrated, the two adjacent links are treated as one link and the number of links is reduced by one. The device moves.
In the link device composed of four links D, W, J, and A, when the door movement is stopped and the door D and the door frame W are integrated, the link device is a triangular link device that does not move. Even in this case, if one of the links is used as a spring or two adjacent links are connected at a sliding corner, the movement becomes possible. For example, FIG. 2 and FIG. 8 are link devices composed of four links. In the case of FIG. 2, by connecting the mounting shaft Sw of the telescopic part at the sliding corner, one link is a spring in FIG. Even if the rotation of the door is stopped by changing the length of the link, the telescopic portion can continue to move.

When the link device in which the rotation around any of the connecting shafts stops and the number of links is reduced by one is composed of four or more links, the link device can move. In the door rotation mechanism, the link device continues to move even when the door is stopped.
In the case of FIG. 27, the case where two adjacent links engage with each other side by side and the two adjacent links extend in a straight line, “rotation around any connecting axis” Has stopped. " Also, as shown in FIG. 26 and FIG. 28, applying a resistance means that “the rotation around any of the connecting shafts is stopped” and the number of links is simulated by a link device having three motions.
In the “link device comprising four or more links” of the present invention, the rotation mechanism having five or more nodes is provided with a releasable restraining means, so that “the rotation around any connecting shaft is restrained”. It is intended to move as a four-bar rotation mechanism, and as the number of links increases, the number of restraint points increases, and several different four-bar rotation mechanisms are possible.
As described above, the link device changes into different forms depending on the degree of freedom and performs different motions. Therefore, even if the door inertia force varies depending on the closing start opening, the motion of the door can be controlled accordingly.

The switchgear shown in each embodiment has a stopping means that keeps the “force acting on the door” small in the “(A) range” and a releasable restraining means that releases the stopping means in the “switching range”. (
A large force is exerted on the door in the “range”. The acting force distance Lo indicates “the distance between the pivot axis O and the acting line of the acting force Fo, and the driving force distance Lv indicates the distance between any of the connecting shafts and the acting line of the driving force Fv.
In each of the operation explanatory diagrams, the plan view shows the upper surface of the door as D and is based on the horizontal plane on which the upper surface of the door moves, but the horizontal plane on which each link moves is not necessarily the same as the horizontal plane on which the upper surface of the door moves. The connecting shaft is a common rotating shaft of adjacent links, and two links are overlapped on the connecting shaft in the figure. W is a door frame to which the door is attached or a wall surface around the door frame. In each operation explanatory diagram, the blank paper surface means the door frame W.
In each operation explanatory diagram, the suffix at the end of the symbol indicates the opening degree Θd of the door, for example, D100 indicates a state of being stationary when fully opened, D90 is the maximum value of the closing opening degree, and the fully opened door, D10 Indicates a door just before closing, and D0 indicates a door when fully closed. For example, FIG. 10A shows a state in which the door D is urged in the direction opposite to the arrow A in the drawing and is stationary. For example, D10 shown in FIG. 5 (c) indicates “the state of the door at the time of latch contact, and D0 shown in FIG. 5 (d) shows the state of the door in which the door D is closely attached to the door contact Gd.
The door frame W is a wall surface of the door frame W and its surroundings, and is a plane including the rotation shaft O and the fixed support shaft SwC, and is a blank sheet surface in the drawing. The plane on which each link of the illustrated link device operates does not necessarily coincide with the “plane including the rotation axis O and the fixed support shaft SwC”, but is a different plane parallel to the plane.
The angle Θak is an angle between the axis A Za of the link A and the sliding surface K, and unless otherwise specified, the wheel B
b indicates the angle on the moving side.
The opening / closing device is a link device that connects the attachment portions of the opening / closing portions D, W and the expansion / contraction portion A by sliding pairs or by turning pairs, and fixing the attachment shaft that attaches to the door D to the connection shaft C and the attachment shaft that attaches to the door frame W. It will be called a support shaft Sw.

Fig. 1 shows the "(A) range" rotating operation that rotates the door with a small force, the "(A) range" sealing operation that rotates the door with a large force, and the "switching range" that switches from a small force to a large force. FIG. 2 is a plan view of the door operation for explaining the switching work and the predetermined opening degree of the door at which the switching work starts, and is a representative drawing detailing the outline of the present invention.
FIG. 1A is a state diagram when the door is fully opened, and FIG. 1B is a state diagram when the door is fully closed. Figure 1
As shown in a), the rotation range in which the door continues to rotate from the fully open position to the fully closed position is the range of “(A)” where the door simply rotates and the range of “(I)” where the door rotates while the latch is recessed. ”. The link device of FIG. 1 includes three links, ie, two opening / closing bodies D and W sharing a pivot axis O and a link A, and the link A is connected to the door D in a sliding pair. The door D, which is one of the two opening / closing bodies, is provided with a connecting shaft C, and a link A is rotatably supported around the connecting shaft C.
A wheel B is mounted on a rotating shaft Ib of the wheel provided at the tip of the link A. A sliding surface K is provided on the door frame W which is the other of the two opening / closing bodies, and the wheel B moves along the sliding surface K. The wheel B is a slider that moves along the sliding surface K, and the wheel B shown in many embodiments is a generic name for the slider. The sliding surface K is a general term for grooves in which the slider moves.

The connection shaft C is provided on a “rotary body Jc that is rotatably supported around a support shaft Cj provided on the door” and is movably attached to the door D. A pressing spring U is interposed between the rotating body Jc and the door D, and the rigidity of the pressing spring U is adjusted in a range from zero to infinity. When the rigidity of the push spring U is infinite, the connection shaft C is fixed to the door D, and the presence of the rotating body Jc and the push spring U becomes irrelevant. In a state where the connecting shaft C is directly fixed to the door D, “(A) rotating means”, “switching means”, and “(I) rotating means” function, and the rotating body Jc and the pressing spring U are added. By
The operation of these means is delayed.
Hereinafter, when the functions of “(A) rotating means”, “switching means”, and “(I) rotating means” are described, the connecting shaft C is described as being directly fixed to the door D. To.

The link A is urged to rotate in the direction of arrow A in the figure by the pulling spring V, and a rotational force Mv acts around the connection axis C. The rotational force Mv is a driving force, and a bending force acts on the link A. The “contact point b between the sliding surface K and the wheel B” has “the force Fb that the wheel B presses the sliding surface K” (hereinafter referred to as “contact point b”). , Referred to as a pressing force Fb). In the closing process from the fully open position shown in FIG. 1 (a) to the fully closed position shown in FIG. 1 (b), the link A rotates around the connecting shaft C in the direction indicated by the arrow A in FIG. The base end Ko
To the end Ke, and the connection axis C moves in the direction of arrow B in the figure along a circle Ro centered on the pivot axis O. A broken line shown in FIG. 1A indicates a state in the middle of closing. For example, C10, A10, and B10 indicate the connecting shaft C, the link A, and the wheel B just before closing. Just before closing, it indicates the vicinity where the opening of the door is approximately 10 degrees, and is an area close to the end of “(A) range” and close to the beginning of “(A) range”.
Since the pulling spring V continues to shrink throughout the closing process, the door continues to rotate from the fully open position to the fully closed position. If the spring that provides the driving force can continue to expand and contract in one direction without stopping, the door will continue to rotate without stopping.

The action line of the pressing force Fb is perpendicular to the sliding surface K and is a straight line passing through the “contact point b between the wheel B and the sliding surface K” and the wheel rotation axis Ib. Moves with the movement of the wheel B. The sliding surface K is a passage that continues from a position close to the pivot axis O to a position far from the axis O, and when the wheel B moves on the sliding surface K from the base end portion Ko to the terminal end portion Ke immediately before closing, the pressing force Fb is reduced. The action line also moves away from the pivot axis O, and the action force distance Lo increases.
In “range (A)” shown in FIG. 1A, the acting force distance Lo is small and the driving force distance Lv is large. The rotational moment Mo acting around the pivot axis O is the product of the acting force distance Lo and the pressing force Fb.
Since the driving force Mv around the connection axis C is the product of the driving force distance Lv and the pressing force Fb, the pressing force Fb
As the line of action approaches the pivot axis O, the rotational moment Mo decreases, and even when the driving force Mv acting around the connecting axis C is large, it is converted into a pressing force Fb. Further, the rotation of the link A around the connection axis C is small, and the rotation of the door D around the pivot axis O is large. Moreover, since the expansion and contraction of the spring is small in the “(A) range”, the force for moving the door is small and the acceleration is small.
In the “range (ii)” shown in FIG. 1B, the acting force distance Lo is large and the driving force distance Lv is small. When the same pressing force Fb is applied, the rotational moment Mo acting around the pivot axis O is proportional to the operating force distance Lo, and when the same driving force Mv is applied, the pressing force Fb is applied to the driving force distance Lv.
Therefore, even if the driving force Mv acting around the connection axis C is small as the wheel B moves away from the pivot axis O, the rotation of the door greatly affects. Further, the rotation of the link A around the connection axis C is large, and the rotation of the door D around the pivot axis O is small. In the "(I) range", the expansion and contraction of the spring is large.
The power to move the door is great and the acceleration is great.

Here, “the acceleration is large in the range of (i)” becomes a problem. Even if the door rotates with a weak force in the "(A) range", the door accelerates if the force continues to be applied to the door. Furthermore, when the vehicle is accelerated in the “range (ii)”, the rotational speed of the door reaches the maximum value when the door is closed. The impact sound at closing is the extra energy converted into sound during the sealing operation, and the kinetic energy of the door at closing is proportional to the square of the rotational speed of the door at closing. "When it accelerates even a little, it comes to emit a loud impact sound. The door of the present invention has a problem of reducing the impact sound at the time of closing, and how to prevent acceleration from becoming large in the “(range)” is an important problem.

In “range (A)” shown in FIG. 1 (a), the link A rotates about the rotation axis Ib of the wheel, the movement of the wheel B is small, and the rotation of the door D is large. In the “(ii) range” shown in FIG. 1B, the link A rotates about the connection axis C, the movement of the wheel B is large, and the rotation of the door D is small. The wheel B performs a circular motion around the connection axis C, the moving direction of the wheel B is the circumferential direction of the circular motion, and the movement of the wheel B is suppressed by the sliding surface K. The force that suppresses the movement of the wheel B rotates the door.
As shown in FIG. 1A, the “circumferential direction of the circular motion of the wheel B” and the sliding surface K are substantially orthogonal to each other in “range (A)” and greatly resist the movement of the wheel B. In order to move the wheel B, the force acting on the door must be large. In addition, the driving force distance Lv is large, and the force of the tension spring V is converted to a small pressing force Fb. As a result, the force of the tension spring V becomes insufficient for a large resistance. The spring with insufficient force expands and contracts slowly without expanding and contracting in a moment, and the wheel B moves slowly and the door D rotates slowly.

As shown in FIG. 1B, the “circumferential direction of the circular motion of the wheel B” and the sliding surface K are substantially parallel in the “(range)”, and the resistance to movement of the wheel B is small. The closer the “angle Θak on the moving direction side of the wheel B at the angle between the sliding surface K and the axial center line Za of the link A, the link B is closer to a right angle than the acute angle”, the greater the movement of the wheel B is. The rotation of becomes smaller. When the angle Θak changes from a right angle to an obtuse angle, the wheel B moves away from the sliding surface K and moves freely.
The shape of the sliding surface K is centered on the position C10 of the connecting shaft C just before closing, and the radius is approximately “the sum of the length of the link A (the distance between the connecting shafts at both ends of the link A) and the radius of the wheel B. When the connecting shaft C passes the position C10, “the wheel B that has been constrained in the vicinity of the pivot O until then” reaches the terminal portion Ke of the sliding surface K in an instant. . In this case, since the wheel B is transferred without any rotation of the door D, the door remains at a position where the opening is 10 degrees.
Assuming that the arc R0 is an arc having the same radius as the arc R10 with the position C0 of the connecting axis C at the closing time as the center, the sliding surface K coincides with the arc R10 at the base end Ko, and the arc at the terminal end Ke When the concave surface coincides with R0, the wheel B leaves the base end portion Ko of the sliding surface K at the moment when the connecting shaft C passes the position C10, and the sliding surface is slightly accompanied by the rotation of the door D. It reaches the terminal end Ke of K. Sliding surface K
Is similar to a straight line with zero curvature at the base end portion Ko and the terminal end portion Ke, and the curvature has a maximum value at the intermediate portion of the sliding surface K. Therefore, the normal line standing at the base end portion Ko and the terminal end portion Ke The axial center line Za of the link A is substantially coincident, the angle Θak is substantially right angle, and the wheel B is easy to move in a state of approximating no load at the beginning and end in the “(range)”, and the movement of the wheel B There is almost no rotation of the door. In the middle part, the wheel B moves while receiving resistance, and the door is slightly rotated. The wheel B becomes difficult to move in the middle, and if it passes the middle, it becomes easy to move and reaches the end portion Ke of the sliding surface K.
Thus, the sliding surface K is provided with restraining means for retaining the wheel B in the vicinity of the pivot O and releasable restraining means for moving the wheel B away from the pivot O at a predetermined opening degree of the door D.

"Rotating means (ii)" has a force to rotate the door by recessing the latch, and is larger than the force of "(a) Rotating means" that simply rotates the door. If the time when the movement starts greatly is before "at the time of latch contact", the latch male part Rd contacts the female part Rw after the "force acting on the door" is converted to a force that rotates the door. The door is sealed with a recess. In this case, the range of rotation of the door after the “force acting on the door” turns into a large force (
In other words, the range of “(i)”) is large and the acceleration of the door becomes large, and a large impact sound is emitted.
In the “switching range”, when the latch male part Rd comes into contact with the female part Rw and at the same time the wheel B starts to move greatly, if the base end Ko of the sliding surface K is a straight line with zero curvature, the “door” Even if the force acting on the door is insufficient to rotate the door, or even if the door stops before closing, the wheel B can move and the wheel B continues to move without stopping. When the terminal portion Ke of the sliding surface K is reached, the “force acting on the door” grows into a force for rotating the door, and the latch is recessed to seal the door. That is, since the “switching means” is not or hardly accompanied by the rotation of the door, the wheel moves with the door almost stopped.
In this case, since the resistance of the movement of the wheel B is not applied when the wheel B starts to move greatly, the wheel B
Reaches the end portion Ke of the sliding surface K in an instant. Moreover, the fact that the rotation of the door does not accompany the movement of the wheel B means that there is no range in the “switching range”, and there is no passage of time between “the range of (A)” and “the range of (I)”. Absent. The “switching means” further accelerates the rotation speed of the door just before closing and makes a loud impact sound.

In the “switching range”, when the wheel B starts to move greatly after the latch male part Rd contacts the female part Rw, when the latch male part Rd contacts the female part Rw, the “(i) rotating means” Before switching
Since the latch cannot be recessed with the force of “rotating means (a)”, the door will not be sealed and will stop.
As shown in FIG. 1 (b), the state reaching the terminal portion Ke of the sliding surface K is "the circumferential direction of the circular motion of the wheel B".
And the sliding surface K are substantially parallel, the pressing force Fb and the axial center line Za of the link A substantially coincide, and the driving force distance Lv is short. Since the driving force Mv around the connecting axis C and the “product of the pressing force Fb and the driving force distance Lv” balance, the pressing force Fb becomes infinite when the driving force distance Lv approaches zero. "
The “switching means” switches the driving force Mv to a very large force even if the driving force Mv is a very small force, but completes the operation with a very small force and switches to a large force in an instant. It becomes a factor to accelerate.
When the “switching range” starts after the latch contact, the drive unit stops and the door also stops. However, it is desirable that the door starts moving again from the state where the door has stopped and is sealed. Therefore, there is a need for a rotation mechanism for a link device that includes a drive unit that continues to move even when the two opening / closing bodies remain stationary.

The “(a) and (ii) rotating means” and “switching means” described above function in a state where the connecting shaft C is fixed to the door D. Next, functions in a state where they are not fixed so as to be movable will be described. The means for connecting the connecting shaft C to the door D so as to be movable prevents the acceleration from increasing in the “range (ii)”.
When the drive unit and the opening / closing unit are interlocked, when one of the drive unit and the opening / closing unit stops, both stop. When not interlocking, even if one of the drive part and the opening / closing part stops, the other may continue to move. As shown in FIG. 1, when the rotating body Jc is rotatably supported around the “support shaft Cj provided on the door” and the connecting shaft C is movably attached to the door, the force of the drive unit is applied to the door. Even when the force of rotating the door is insufficient and the door remains stationary, the rotating body Jc rotates in the direction indicated by the arrow C in the figure by the “reaction force of the wheel B pressing the sliding surface K”.

The rotating body Jc is urged by the push spring U in the direction opposite to the arrow C in the figure, and rotation in the direction opposite to the arrow C in the figure is prevented by the hitting Ga. The amount of rotation of the rotating body Jc changes depending on the magnitude of the pressing force Fb, but also changes depending on the rigidity of the pressing spring U, and the resistance applied to the movement of the wheel changes.
When the rigidity of the push spring U is zero, the urging force of the spring is not transmitted to the door, and the door continues to move with inertial force. Regardless of whether the "switching range" starts before or after the latch contact, even if the pressing force Fb is small, the rotating body Jc rotates and the link A also rotates slightly, so that the "sliding surface" The angle Θa ”between K and the axis A of the link A shifts to the obtuse angle side. The sliding surface K changes to the downward slope side with respect to the moving direction of the wheel B, and becomes easier to move as the wheel B moves, and reaches the end portion Ke of the sliding surface K without the door D rotating. If the mounting shaft of the drive unit and the opening / closing body can be moved, a “switching means” is provided that causes no or little rotation of the opening / closing body.

When the rigidity of the push spring U is infinite and the mounting shaft between the drive unit and the opening / closing body does not move, the “switching range” is after the latch contact, and when the latch contact, “(A) rotating means” If the shape of the base end portion Ko of the sliding surface K is the above-mentioned circle R10, or a curved surface or straight line having a smaller curvature than the circle R10, the moment when the connecting axis C passes the position C10, The wheel B ”constrained in the vicinity of the pivot axis O reaches the end of the sliding surface K all at once, and the wheel B moves without pressing the sliding surface K. When the wheel B moves without pressing the sliding surface K, the drive unit and the door do not work together, and the door D
Does not rotate. “The sliding surface K in which the angle Θa between the sliding surface K and the axis A Za of the link A on the moving direction side of the wheel B” is an obtuse angle causes no or little rotation of the opening / closing body. Switching means "
It is. Thus, when the rigidity of the push spring U is zero or infinite, there is no spring, and the “switching means” does not involve the rotation of the opening / closing body at all or almost, and the “(i) rotation means” Accelerate ".

Depending on the rigidity of the push spring U, the movement of the wheel B and the rotation of the door D are slightly interlocked, and the driving force Mv acting around the connecting shaft C is “the force that rotates the door” and “the force that expands and contracts the push spring U”. The sliding surface K has a curved surface with a larger curvature than the circle R10, and the latch male part Rd contacts the female part Rw and the door stops at the moment when the connecting shaft C reaches the position C10. Even if there is no force to rotate the door in the “force acting on the door”, if the rigidity of the push spring U is set to be small, the push spring U will expand and contract while the door is stopped. Wheel B even when stopped
Can move. The drive and door do not work together.
For example, when the shape of the sliding surface K is the arc R10 shown in FIG. 1A or closer to a straight line than in the case of the arc R10, the curvature increases from the proximal end Ko to the terminating end Ke of the sliding surface K. Become. When the wheel B approaches the base end portion Ko of the sliding surface K, it receives a large resistance, but the wheel B slides toward the terminal end Ke away from the base end portion Ko of the sliding surface K with respect to the moving direction of the wheel B. The gradient of the moving surface K changes to a downward gradient, and the wheel B becomes easier to move. The wheel B is difficult to move at the beginning of the “(range)”, and the elapsed time of the “(range)” is extended so that the inertial force disappears. Further, the wheel B is easy to move at the end of the “(range)” and reaches the end portion Ke even when the spring force is weakened, the driving force distance Lv is small, the acting force distance Lo is large and the weak spring force is reduced. It comes to act strongly on the door.

When the wheel B moves toward the end portion Ke of the sliding surface K while pressing the sliding surface K, the pressing spring U is contracted while rotating the rotating body Jc, and the wheel is loaded. Move slowly. When the force is stored in the push spring U and the force of the push spring U reaches the force to dent the latch, the latch is recessed and the door is opened again even before the wheel B reaches the end portion Ke of the sliding surface K. Start to move. When the latch is recessed, the length of the push spring U extends and the door moves. The movement of the wheel B becomes slow, and the “force for rotating the door” of the driving force Mv hardly increases, and the latch is recessed by the force of the push spring U. There is no excess or deficiency in the force to dent the latch, and the impact sound is reduced.
The contact Gk attached to the terminal portion Ke of the sliding surface K is a locking means for adjusting the stop position of the wheel B. By stopping the movement of the wheel B, it is sealed only by expansion and contraction of the push spring U.
The position where the push spring U is fully extended is the fully closed position of the door. Depending on the position where the push spring U is fully extended, the door does not necessarily reach the position where it abuts against the door. This makes it possible to stop the door at “the fully closed position whether or not to contact the door stop” depending on the adjustment of the stop position of the wheel B, and the impact noise is minimized.

The working force on the moving door is small and the working force on the stationary door is large. Since the “force acting on the door” at the time of latch contact becomes stronger than before the time of latch contact, the push spring U starts to shrink after the latch contact. That is, the latch male portion Rd is prevented from coming into contact with the female portion Rw after the “force acting on the door” is switched to a strong force. The amount of expansion / contraction of the push spring U varies depending on the magnitude of the “force acting on the door”, and there are a state in which the push spring U is stretched and a state in which the push spring U is contracted at the time of latch contact. The amount is different. Since the greater the inertial force attached to the door in the “(A) range” (hereinafter referred to as “the door inertial force”), the door can rotate with a smaller force.
The “force acting on the door” becomes small, and the “gap δjd between the rotating body Jc expanded by the push spring U and the door D” becomes wide in a state where the push spring U is extended at the time of latch contact. The larger the door inertia force, the more the push spring U needs to be contracted and the rotating body Jc needs to be rotated more greatly. The deceleration effect of the push spring U is proportional to the door inertia force.

When the push spring U contracts and the latch starts to dent, if the rotation of the link A is stopped, the link spring does not move until the latch starts to dent and the door is fully closed, and the push spring U only extends. In operation, the door is sealed. In a state where the push spring U is contracted at the time of latch contact,
Even when there is no process of contracting the extended push spring U, it takes a long time for the push spring U to extend and seal, and the door is sufficiently decelerated and sealed.
In this way, the link device is equipped with a “driving unit that keeps moving even when the door is stopped” by the “means for fixing the connecting shaft C to the door D”, and “switching with little or no rotation of the door”. Means ". "Means for fixing the connecting shaft C to the door D so as to be movable"
By adding a spring, the “(i) rotating means” is improved to be tightly sealed while decelerating.

The opening and closing device of FIG. 1 is designed to have a deceleration effect so that the door is stopped only by the resistance of the latch just before closing, and the driving force is maintained while the latch is in contact with the door frame and the door is stopped. Mv's “force to rotate the door” causes the force to be stored in the push spring U without rotating the door at all. For that purpose, it is necessary to close at a low speed in the “(A) range” and to reduce the closing speed just before the closing.
By adding a spring to the “means for movably fixing the connecting shaft C to the door D”, the driving force
The means for transmitting Mv indirectly to the door D via the spring U has a deceleration effect even in “(A) range”, and the two springs that urge the door in the same direction interfere with each other and alternately Repeat expansion and contraction. The deceleration effect is particularly remarkable when the door starts to close.

When the door starts to close, the link A is rotated by the pulling spring V. However, since the static inertia acts on the door, the push spring U is contracted without rotating the door. The rotational resistance acting on the pivot axis O of the stationary door is the maximum static frictional force around the pivotal axis O. When the force of the push spring U reaches the maximum static frictional force, the door starts to move, and the maximum resistance around the pivotal axis O The static friction force is drastically reduced to the kinetic friction force. As a result, the force of the push spring U is extended until it decreases to the kinetic friction force. Link A during this time
The movement of the wheel B and the movement of the wheel B are almost stopped, and the door moves as the push spring U extends. That is, the door which has started to move rotates with a force having a magnitude approximate to the kinetic friction force. At the beginning of the door movement, when the push spring U is extended and the force is lost, the wheel B starts moving and the amplitude at which the push spring U contracts again is repeated. . This tendency becomes more prominent as the force of the tension spring V and the push spring U is smaller, and this amplitude disappears in several times. At the time of latch contact, the push spring U extends greatly in proportion to the magnitude of the force of “(A) rotating means”, and “wheels” with respect to the rotation amount of the door from the time of latch contact to the fully closed state. B is accompanied by a large movement ”. As a result, the wheel B is in the vicinity of the base end portion Ko of the sliding surface K at the time of latch contact, and is switched to “(i) rotating means” after the latch contact.

In the middle of “range (a)”, the push spring U contracts, and the force acting on the door is a force that balances “the sum of the kinetic frictional force around the pivot axis O and the air resistance received by the door”. Moves at a constant speed without acceleration, and if the force acting on the door is more than that, the door will accelerate. In order to reduce the acceleration in the middle of “range (a)”, it is preferable to rotate the door with a weak force. Further, since the strain energy of the spring replaces the movement of the door, it is desirable to reduce the amount of expansion and contraction of the spring as much as possible in order to reduce the acceleration of the door.
1 has one side Sd attached to the rotating body Jc and the other side Sa attached to the link A. One side Sd is provided at a position near the rotation axis C of the link A, and the other Sa is the link A. Is provided at a position far from the rotation axis C. This reduces the expansion and contraction of the spring accompanying the rotation of the link A. The smaller the spring expansion and contraction, the smaller the acceleration of the door, so that the door will not rotate without expansion and contraction of the spring.

When a bending force acts on the link A as shown in FIG. 1, the contact b between the sliding surface K and the wheel B slides on “the circular motion of the wheel B in the direction of arrow A in the figure about the connection axis C”. The point that the surface K blocks,
When the connection axis C moves on the circular orbit Ro in the direction indicated by the arrow B in the drawing within the range (A), the contact b does not necessarily move from the base end Ko of the sliding surface K toward the end Ke. Absent. "(Ah)
In the "range", the wheel B is generally stopped in the vicinity of the pivot axis O. However, the link A rotates around the rotation axis Ib of the wheel at the beginning of the "(range)" Parallel to the end and approach the door stop Gd. In some cases, the wheel B approaches the base end portion Ko of the sliding surface K together with the connecting shaft C.
As the movement of the link A shifts from the rotational movement to the parallel movement, the “rotation in the direction of the arrow A in the drawing around the connection axis C of the link A” gradually decreases, and the amount of contraction of the tension spring V also decreases. In some cases, the link A rotates in the direction opposite to the direction indicated by the arrow A in the drawing to extend the pulling spring V, and the pulling spring V biases the door in the opening direction. Further, the approach of the wheel B to the base end portion Ko of the sliding surface K reduces the acting force distance Lo, which leads to a lack of force in the rotation of the door.
When the shape of the sliding surface K is concave toward the wheel B and the curvature increases as it goes from the proximal end Ko to the terminal end Ke of the sliding surface K, the wheel B is brought into a position before closing before the latch contact. As the wheel B approaches the terminal end Ke in the “(range)” range, the sliding surface K increases in the upward direction with respect to the moving direction of the wheel B. As a result, the “power to rotate the door” is insufficient.
As described above, the opening / closing device of FIG. 1 includes a speed reduction means for reducing the “force acting on the door” just before closing.

Closing the door while applying resistance is to reduce the “force that rotates the door” by the force in the opposite direction, and is simply a means of weakening the acting force. The “force acting on the door” at a position where a large speed reduction means is taken is reduced to be smaller than the force for rotating the door, and the stationary door at this position remains stationary. It is one mechanism that keeps the door open at a slightly opened position, and it can respond to an outsider with the door opened a little, but this "position to reduce the force acting on the door by applying resistance" Is the “(A) range” in the closing process, but it is the “(A) range” in the opening process. Even if the closed door is opened and the hand is released at this position, A greater force than the “reduced size” acts on the door.
Since the push spring U is attached to the door of FIG. 1, the push spring U contracts at the beginning of opening, and then the wheel B returns backward along the sliding surface K. Accordingly, the opening degree of the door when the wheel B returns to the base end part Ko of the sliding surface K in the opening process, and the opening degree of the door when the wheel B moves away from the base end part Ko of the sliding face K in the closing process. In contrast, the wheel B is located at the terminal portion Ke of the sliding surface K in the closing process “(
In the opening process, the “(range)” in which the wheel B is located at the terminal end Ke of the sliding surface K becomes larger than the “range (ii)”. (Hereafter, the range including the “(A) range” of the closing and the “(A) range” of the opening process will be referred to as the “(A) range”). "Position" is a position where a large force is applied to the door when the door is opened, and the door does not remain stopped even if the hand is released from the door. Therefore, it always closes when you release your hand, and never stops and stays open.
The opening degree of the door that the “switching means” works in the process of opening the door is the case where the door is opened widely and the hand is released to rotate with a weak force and then switched to a strong force, and the door is opened slightly and the hand is released. This is a position for separating the form of the closing process when rotating with a strong force.
By adding the push spring U in this way, the degree of freedom of the link device is increased, and the form is different from the case where the movement of the door follows the movement of the driving part and the case where the movement of the driving part follows the movement of the door. A difference in the form of the link device will be recognized when the door is closed and when the door is opened.

In order to reduce the acceleration even in the “(ii) range”, it is better to reduce the force of the “(ii) rotating means” as much as possible, and it is desirable to convert the force of a small spring into a large sealing force.
The sealing operation of the present invention has a feature of a so-called wedge effect that decomposes a weak force acting in the moving direction of the connecting shaft into two strong forces acting substantially perpendicular to the moving direction. The sealing operation in FIG. 1 is performed by applying a weak force in the moving direction while the rotating shaft Ib of the wheel on which the pressing force Fb acts moves along a track substantially perpendicular to the tangent of the circle centering on the pivot O of the door. It is broken down into two forces that work approximately at right angles to each other, and one of the two forces is supported by the door D and the other by the door frame W, and the weak force in the moving direction is expressed as “two strong forces approximately perpendicular to the moving direction” Convert to
At the time of sealing, the wheel B moves with a weak force in the circumferential direction of the circular motion, and a large force is exerted in the radial direction. The weak force in the moving direction is converted into two sealing forces close to infinity, and since the angle Θak is substantially a right angle at the time of sealing, the action lines of the two forces are arranged in a substantially straight line and substantially coincide. One is supported by a rigid body A that does not move on the door and the other. The sealing force becomes close to infinity because the part that supports it does not move.
A pressing spring U is inserted into a portion supported by the rigid body A that does not move. The pressing spring U allows a predetermined sealing force to act on the door at a predetermined rotation angle of the link A.

The switchgear of FIG. 1 processes a weak force of “(A) range” and a strong force of “(A) range” with one spring, and an acting force distance Lo in “(A) range”. The force of the spring is kept small while reducing the force acting on the door by moving the shaft closer to the pivot axis O, and the spring force is minimized by keeping the acting force distance Lo away from the pivot axis O in the “(ii) range”. At the end of the turn, a large force is applied to the door. Even with a single spring, the “force acting on the door” can be freely designed according to the shape of the sliding surface K. Also, the force acting on the door when closing is the same as the force when opening the door and the direction is the opposite, the door that closes with a small force can be opened with a small force, when opening the door It feels light.
The wheel B that moves with a small force along the sliding surface K while applying a large force to the door at the time of closing like the opening and closing device of FIG. 1 does not reverse unless a large force is applied when the door is opened. . However, in the process of closing the door, the angle Θak is an acute angle and is highly resistant to wheel movement, and in the process of closing the door, the angle Θak is an obtuse angle and not resistant to wheel movement. Despite the strong force acting on the door during the closing process, it feels light when opening the door.
In order to press the door D against the door stop Gd at the terminal end Ke to which the wheel B has been transferred, the angle Θa needs to be an acute angle. In addition, since the wheel B does not reverse when the angle Θa is not an acute angle when opening the closed door in FIG. Even when a strong force is applied to the door during sealing, it feels light when opening the door.

As described above, the door of the present invention always stops right before closing and always closes when the door starts to close regardless of where the hand is released. Is not transmitted to the door at all or almost so that the door stops or is in a state close to it, and then the "power to rotate the door" is increased from zero to "power to seal the door" In this case, the door starts to move again, and the drive unit keeps driving even when the door stops. The factor that stops without permission is the lack of power to rotate the door, and there is a feature in that "sealing work that requires a large force" is possible even with insufficient power,
When the door accelerates, even if the force is insufficient, the door may not stop immediately before closing, and a means for preventing the door from accelerating is required.
The present invention provides a means for preventing the door from accelerating even if the closing speed before closing is large, such as when the strength of the spring is too strong for some doors. Decrease the speed so that the latch resists the restart of the door in the “switching range” so that the latch is recessed with a small force, and the required time is extended in the “(range)” so that the inertia force of the door disappears. It is to make.

FIG. 2 is a plan view for explaining the operation of “deceleration means for preventing acceleration”. The speed reduction means attached to the opening / closing apparatus of FIG. 2 reduces the inertia force of the door, and the opening / closing apparatus shown in FIG. In place of the link A of the drive unit in FIG.
The link A is connected to the door D in a sliding pair, and has the same operation and function as those in FIG. 1 while the sliding surface K is shorter and smaller than that in FIG. A compressive force acts on the link A.
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. The connecting shaft P at the base end of the link A is connected to the rotating body J. The rotating body J is rotatably supported around a connecting shaft C provided on the door D, and is urged to rotate in the direction of arrow A in the figure by a pulling spring V. In the process of closing the door, the “intersection angle Θaj of the axis core line Zj of the rotating body J and the axis axis line Za of the link A” decreases, and the wheel B presses the “sliding surface K provided on the door frame W”. The connection axis C moves in the direction of the arrow B in the figure along the orbit of the circle Ro centered on the pivot axis O.

In the case of FIG. 2, unlike the case of FIG. 1, a compressive force acts on the link A, and the wheel B can move to the obtuse angle side of the angle Θak. Stop. In the case of FIG. 1, a bending force acts on the link A, the wheel B moves on the sliding surface K regardless of the angle Θak, and the force acts so that the angle Θak moves to an acute angle, and the door is moved while moving. Rotate. In contrast, in the case of FIG. 2, a compressive force acts on the link A, the wheel B moves to the obtuse angle side of the angle Θak, and the obtuse angle side movement at the end of the sliding surface K is prevented. It stops at either end of the sliding surface K and does not stop in the middle of the sliding surface K. In the case of FIG. 2, force acts so that the angle Θak moves toward an obtuse angle, and the door is rotated while the movement is blocked.
As shown in FIGS. 2A and 2B, the angle Θak is maintained at an acute angle in “range (A)”, and the wheel B stops at the base end portion Ko of the sliding surface K. When the angle Θak exceeds 90 degrees as the door D rotates in the “switching range”, the wheel B begins to move to the obtuse angle side toward the terminal end Ke of the sliding surface K as shown in FIG. As the wheel B moves, the angle Θak increases, and FIG.
When the wheel B reaches the terminal end Ke of the sliding surface K as shown in FIG.
The broken line in FIG. 2 (a) indicates the fully opened state, and the pressing force Fb90 is urged in the door opening direction, and the stationary state can be maintained by stopping the door opening direction at the previous side door not shown. I can do it.

In the case of FIG. 1 in the closing process and the opening process, the wheel B is a reversible device in which the movement of the link device is reversed only when the direction of rotation of the door is reversed. The wheel B reciprocates in different paths in the closing process and the opening process, and the link device is a non-reciprocal device.
When the wheel B is at the end portion Ke of the sliding surface K, the angle Θak is acute in the case of FIG. 1 and the door cannot be opened if the angle is obtuse, but in the case of FIG. At Ke, the angle Θa
k is an obtuse angle, and the rotating body J rotates in the direction opposite to the arrow A in the figure, and the angle Θak shifts to an acute angle. The “crossing angle Θak between the sliding surface K and the axis A Za of the link A” in the direction in which the wheel B returns becomes an obtuse angle, and the wheel B can return to the base end portion Ko of the sliding surface K. Unlike the case of FIG. 1, the opening degree of the door when the wheel B returns to the base end portion Ko of the sliding surface K in the opening process is the same as that when the wheel B moves away from the base end portion Ko of the sliding surface K in the closing process. It is much larger than the opening of the door. That is, “(
The range of “Ai” is much larger.

In “(A) range”, the wheel B is stopped at the base end portion Ko of the sliding surface K, and the connecting shaft P is connected to the base end portion K.
It moves along a circle Rko centered on the rotation axis Ib of the wheel that stops at o. "Range of (I)"
The odor wheel B stops at the end portion Ke of the sliding surface K, and the connecting shaft P moves along a circle Rke centered on the rotation axis Ib of the wheel stopped at the end portion Ke. As shown in FIG. 2A, in the “range (A)”, the acting force distance Lo is small and the driving force distance Lv is large. Therefore "force acting on the door"
Is small. Further, as shown in FIG. 2D, in the “(range)”, the acting force distance Lo is large and the driving force distance Lv is small. Therefore, the “force acting on the door” is large. In the case of FIG. 2, not only the acting force distance Lo is increased by moving the wheel B away from the pivot axis O, but the axis line Za of the link A and the axis line Zj of the rotating body J are arranged in a straight line. As a result, the driving force distance Lv becomes smaller, and the “force acting on the door” becomes larger when sealed.
Thus, the sliding surface K is provided with a releasable restraining means for stopping the wheel B at the base end Ko, and by connecting one of the connecting shafts with a sliding pair, the structure of the link device and the form of motion are “ There are two differences between “range (a)” and “range (ii)”.

As shown in FIG. 2, the point of action of the force acting on the door in the “(range)” is smaller than the distance away from the pivot O as compared with the case of FIG. Unless "Fb" is made larger than in the case of FIG. 1, the force when the latch is depressed is not the same. If the “force acting on the door” is the same, the movement of the door is the same, and the force when opening the door is the same. Regardless of the structure and operation of the link device and the force of the spring, if the resulting weak force is applied to the door, the door closes slowly so that the door does not feel heavy when opened. Become.
In order to reduce the size of the device, it is necessary to increase the force of the spring. By increasing the force of the spring, the rotational resistance acting on each link connecting shaft and the rolling friction around the rotating shaft of the wheel B increase. This makes the link device difficult to move. As a result, the spring force must be increased further. If the spring force is increased, it is necessary to make the portion that supports the spring force strong, and if the force applied to the door is reduced by downsizing the device, a large force is applied to the “portion that attaches the device to the door or door frame”. Since it works, it is necessary to make the door or door frame of the attachment part sturdy.

Considering the case where the sealing wheel BB is attached to the rotating body J as shown in FIGS. 2C and 2D and the sliding surface Kb moving along the same is provided on the door frame W, “the wheel Bb is the sliding surface. The distance Lob between the line of action of the force Fbb that presses Kb and the pivot O increases. "Force acting on the door" when sealed
Since the point of action of this is transferred to a position far away from the vicinity of the pivot axis O, a small spring force can be applied to the door, and compared with the case where the sealing wheel BB is not attached to the rotating body J, Strength can be reduced.

The sliding surface K is rotatably supported around the support shaft Ik, and is urged by the push spring Uk about the support shaft Ik in the direction opposite to the arrow C in the figure. As shown in FIG. 2A, when the force for rotating the door is small in the “range (A)”, the force acting on the push spring Uk is also small, the push spring Uk is extended, and the sliding surface K hits Gk. Engage. Even if the sliding surface K does not engage with the contact Gk, the distance between the sliding surface K and the contact Gk becomes smaller, and the angle Θak becomes sharper as the door inertia force increases.
As the door closes, the inertial force of the door increases, the door moves with a smaller force, and the push spring U strongly presses the sliding surface K. As shown in FIG. 2B, the larger the door inertia force at the time of latch contact, the larger the push spring U extends, and the wheel B becomes difficult to move toward the terminal portion Ke of the sliding surface K. This means that “when leaving the base end Ko of the moving surface K” is delayed, the sealing operation is delayed in proportion to the door inertia force, and the braking force in proportion to the magnitude of the door inertia force is applied. Yes.
If a resistance is applied to the movement of the door at the time of latch contact, the “force acting on the door” increases so that the voltage increases due to the resistance. As shown in FIG. 2 (c), even if there is no force to rotate the door at the time of latch contact and the pressing force Fb is small, the sliding face K rotates slightly so that the angle Θak shifts from a right angle to an obtuse angle side. The sliding surface K changes to the down-gradient side with respect to the moving direction of the wheel B, and becomes easier to move as the wheel B moves. As shown in FIG. It moves to the terminal part Ke of the sliding surface K in an instant and stops.

When the wheel B moves on the sliding surface K, in the case of FIG. 1, it moves while pressing the sliding surface K and the expansion and contraction of the push spring U proceeds at the same time. With progress, Figure 2
In this case, the sliding surface K moves in an instant without almost pressing the sliding surface K and without contracting the pressing spring U, and the expansion and contraction of the pressing spring U proceeds with a delay. When the wheel B stops at the terminal end Ke and the “force acting on the door” reaches the “force to close the door,” the expansion and contraction of the push spring U starts.
The “force Fb that the wheel presses the sliding surface” does not require a large force when the door moves and is in a kinematic balance state, and the above-mentioned push force is applied when the door stops and is in a structural mechanical stationary state when the latch contacts. A large force of pressure Fb is generated. The difference between the kinematic balance state and the structural mechanical stationary state is the difference between the state in which the link device is easy to move and the state in which the link device does not move. The greater the power, the greater the power. As the push spring U contracts, the “force acting on the door” gradually grows while becoming more solid and difficult to move.
In the case of FIG. 1, the mounting shaft movably attached to the door is on the door D side, and in the case of FIG. 2, it is on the door frame W side. By extending, the latch starts to dent, and the sealing operation is delayed.

In the case of FIG. 2, the axial center line Za of the link A rotates around the wheel rotation axis Ib throughout the closing process, but the wheel B does not move and the “action line Fb of the force acting on the door” is “sliding surface”. The normal distance established at the point of contact “b” between K and the wheel B ”, and the acting force distance Lo is substantially constant. As in FIG. 1, there is no means for reducing the closing speed by reducing the acting force distance Lo just before closing or by receiving resistance when the wheel B moves along the sliding surface K. In the case of FIG. 2, the speed reduction means is attached separately from the drive unit.
In FIG. 2, the speed reduction means is shown on the door handle side of the opening / closing device. Wheel Bb is link Aa
The connecting shaft Pp, which is mounted on the rotating shaft Ibb of the wheel provided at the distal end portion of the shaft and provided at the base end portion of the link Aa, is connected to the rotating body Jj. The rotating body Jj is rotatably supported around a connection shaft Cc provided on the door D, and is urged by a pressing spring Uu in a “direction in which the rotating body Jj contacts the contact Gj provided on the door D”. The link Aa is urged by the pulling spring Vv in the “direction in which it abuts against the contact Ga provided on the rotating body Jj”.

As shown in FIG. 2A, when the wheel Bb does not come into contact with the sliding surface Kk, the rotating body Jj comes into contact with Gj and the link Aa comes into contact with the contact Ga and stands by in “range (A)”. . As shown in FIG. 2B, when the wheel Bb comes into contact with the sliding surface Kk, the initial contact is “on the side where the wheel Bb moves at an angle between the axial line Zaa of the link Aa and the sliding surface Kk”. The angle Θakk ”is an acute angle, and there is no rotation of the link Aa in the direction of arrow E in the figure, and the rotation of the rotating body Jj in the direction of arrow D in the figure precedes. As shown in FIG. 2 (c), the angle Θakk changes from an acute angle to an obtuse angle according to the rotation of the rotating body Jj, and the link Aa rotates in the direction indicated by the arrow E in the figure. As shown in FIG. 2D, when the axial center line Zaa of the link Aa and the sliding surface Kk become substantially parallel, “the force Fbb that the wheel Bb presses the sliding surface Kk becomes weak and resists the door closing direction. Disappear.
The speed reduction means in FIG. 2 consists of two rotations, the rotation of the link Aa and the rotation of the rotating body Jj. The speed reduction effect due to the rotation of the link Aa in the direction indicated by the arrow E in FIG. Therefore, the state where the angle Θakk is an obtuse angle is kept long by the rotation of the rotating body Jj in the direction indicated by the arrow D in the drawing.
The two rotations have a restoring force, and the two rotating restoring forces will cause the door to rotate in the opening direction, but if the force acting in the direction of closing the door exceeds this, the rotation in the door opening direction will be blocked. Is done. Further, the speed reduction means in FIG. 2 does not function over a large rotation range of the door, but functions in a narrow limited range, and can function only in the “range”. The “switching range” is a small rotation range of the door, but the movement of the drive unit is large, and the speed reduction means of FIG. 2 can be incorporated.

The door that rotates in the rotation range in which the speed reduction means operates has a "door closing force and door inertia force" acting in the direction in which the door closes, and in the opposite direction, "door rotation resistance and speed reduction device. "Braking force" works. “Door rotation resistance” is “the force that barely starts to move so that the door does not remain stationary”, and “the braking force of the reduction gear” from “the force that the drive unit closes the door and the door inertia force” Rotates when the "remainder force" is less than the "door rotation resistance".
There is no inertia of the door at the position where the door is opened and the hand is released.
When the “excessive force” obtained by reducing the “braking force of the speed reducer” is larger than the “door rotation resistance”, it rotates without remaining stopped. When the “braking force of the speed reducer” is set to zero, when the “force that the drive unit closes the door” is larger than the “door rotation resistance”, the motor does not stop and rotates.
Further, if the “braking force of the speed reducer” is increased rather than zero, the door remains stopped unless the “force that the drive unit closes the door” is increased by the amount corresponding to the increase of the braking force of the speed reducer.
In this way, if the braking force of the reduction gear is increased, the "braking force of the increased reduction gear" is added and the "force that the drive unit closes the door" is not increased as much as possible. You can't keep it from stopping when you let go.
Increasing the braking force of the reduction gear has nothing to do with the door inertia force, and has no effect of reducing the door inertia force.

Consider the "braking force of the reduction gear" as zero. The “door rotation resistance” acting on the stationary door is the maximum static friction force, which is larger than the kinetic friction force acting on the rotating door. The force to start the stationary door is more than the maximum static friction force, and when the door starts to move, more force is applied to the door than necessary. The door that starts to move is driven by the “driving force greater than the maximum static frictional force and the inertial force of the door”, and the kinetic frictional force acts against this. “Door does not stop wherever you release your hand” does not stop when it starts moving.
On the accelerated door, a “driving force greater than the maximum static frictional force and a door inertia force” act, and against this, a kinetic frictional force and “air resistance received by the door surface” act. When the “air resistance received by the door surface” increases and the former and the latter become balanced, a constant velocity motion without acceleration is obtained. If a slight resistance is applied at this time, the “sum of the kinetic frictional force and the air resistance and resistance received by the door surface” will be larger than the “driving force greater than the maximum static frictional force and the door inertial force”, and the constant velocity motion will slow down. . When the door is stopped by applying a larger resistance, the “resistance” is larger than the “driving force exceeding the maximum static frictional force”. The result is the same when “driving force greater than the maximum static frictional force” is reduced instead of “resistance”.

Whatever the force acting on the door before the latch contact or the closing speed of the door,
It is an object to make the state where the influence of the inertial force of the door is removed as much as possible when the door is stopped or close to the latch contact. Therefore, when the difference between the maximum static frictional force and the kinetic frictional force is small, or when the air resistance received by the door surface is large and the "driving force greater than the maximum static frictional force" is small, the acceleration of the door is small. It is only necessary to change the “force acting on the door” from small to large without applying a “resistance” at the time of latch contact or reducing the “driving force greater than the maximum static frictional force”.
However, when the difference between the maximum static frictional force and the dynamic frictional force is large and the air resistance received by the door surface is small, if the "driving force greater than the maximum static frictional force" is large, the acceleration of the door is large. It is necessary to take a measure to apply "resistance" or reduce "driving force greater than the maximum static frictional force" to stop or close the door.
Even if the resistance is applied in the “range” and the moving door is stopped, the position where the resistance is applied in the “range” of the closing process is “( I) range "
If (i) rotating means "acts, and the resistance is smaller than" (ii) rotating means ", the door remains stationary no matter where the door is opened and released. Never become. Only in such a case, the resistance works to remove the inertial force of the door.

The door inertia force differs greatly depending on whether the position where the door is opened and the hand is released is the fully open position or the slightly opened position. When the resistance is increased to the same level as the door inertia force when the hand is released in the fully open position,
If the closing speed is suddenly reduced within the short range of “Ai”, a collision occurs, and the impact at the time of closing is just moved to the front of the door. In the present invention, this impact is received by a spring, and the inertial force of the door disappears over time while absorbing the movement in the closing direction of the door by the expansion and contraction of the spring. In addition, because the elastic spring is restored and the door does not return in the opening direction.
(Ii) "Rotating means".
If the resistance is increased as much as the door inertia force when the hand is released in the fully open position, the door inertia can be extinguished to deal with all the door inertia forces ranging from small to large regardless of the opening degree of closing. I can do it. The expansion and contraction of the spring is small when the door inertia force is large and small when the door inertia force is large, but if the “(i) rotating means” is also increased by the amount of the resistance, the “(ii) rotating means” When the inertia force is large and the spring expands and contracts, the expansion and contraction is completed while suppressing the restoration of the spring. Further, even when the inertial force is small and the expansion and contraction of the spring is small, the expansion and contraction of the spring is completed. When opening the door, the elastic spring is biased in the opening direction, so the “force required for opening” is not increased.
Applying a large resistance in the “switching range” where the door and the drive unit do not interlock,
If the “rotating means” is increased, the large resistance disappears regardless of the opening of the door closing, and the inertia of the door disappears without stopping the drive unit. Can keep moving until the door is sealed.

The resistance loaded in “(A) range” simply weakens “(A) rotating means”
The movement of the door, which appears to be decelerated by loading the resistance, is the same as the movement of the door rotating with the weak “(a) rotating means”, and the resistance is ineffective against the door inertia force, "
When the resistance loaded in “(A) range” in “Switching range” is removed in “(A) range”,
Even if there is no change in the magnitude of “the force that the drive unit closes the door”, the “force that acts on the door” changes from small to large.
For example, the air resistance acting on the door surface increases as the door closes, but if the air resistance acting on the door surface is greater than the force to dent the latch before the latch contact, the air resistance is overcome and the door is rotated. The "force that the drive unit closes the door" is greater than the force that dents the latch,
When the latch comes into contact with the door frame W and the door is decelerated at the same time and the air resistance gradually decreases, the “force acting on the door” gradually increases from zero to the “force that dents the latch”. However, at the time of latch contact, “the sum of the force that the drive unit closes the door and the inertia force of the door” is smaller than “the sum of the air resistance and the force that causes the latch to be recessed”, and the latch contacts the door frame W and the door latches at the same time. This is true if the is not recessed.

FIG. 22 shows this embodiment, where the movement of the drive unit stops before the latch contact, and the latch is depressed by the force of the push spring U instead of the “force of the drive unit closing the door”. If the force of the push spring U is adjusted to “the force to dent the latch” and the door inertia force is canceled out by the air resistance, the impact sound is reduced.
FIG. 3 provides resistance in the “(A) range” that is equivalent to this air resistance. Figure 3 shows “(
It is an operation explanatory plan view in the case where resistance is reduced by applying resistance to “(i) rotating means” in “range a” and disappearing in “switching range”. The following FIGS. 3 and 4 illustrate the "(A) range" deceleration, FIGS. 4 to 6 illustrate the deceleration before the latch contact, and FIGS. 7 to 10 describe the "(A) range" deceleration. .
The effect is so great that the speed reduction means is taken near the fully closed position, and the impact sound can be reduced only by the speed reduction means taken near the fully closed position, but it is effective in the range where the door inertia force is small. If the door inertia force is small before and there is no deceleration means, it will not be effective.

The closing device shown in FIGS. 1 and 2 is attached to the outer door surface of the outer door, and FIG. 3 is attached to the inner door surface of the outer door. The inner surface of the door is the surface facing the door frame W of the door, and the space area sandwiched between the inner surface of the door and the door frame W is a space where passers-by enters and exits. It has the advantage that it is not exposed to wind and rain, and the advantage of security.
A “resistance comparable to the above-mentioned air resistance” is attached to the outer surface of the door in FIG. 3, and a driving unit for closing the door is attached to the inner surface of the door. The resistance attached to the outer surface of the door shown in FIG. 3 is obtained by attaching a plurality of reduction gears shown in FIG.
2 operates only when the door is fully opened, and does not function when the closing start opening is less than or equal to the fully open position. Even when the decelerating means operates at an opening degree that is less than or equal to the fully open position, it functions when the opening degree is equal to or greater than the opening degree and does not function when the opening degree is equal to or less than the opening degree.
FIG. 3 includes a speed reduction means 1 that operates at a fully open degree, a speed reduction means 2 that operates at a predetermined opening degree that is less than or equal to a fully open position, and a speed reduction means 3 that operates at an opening degree that is less than or equal to the predetermined opening degree. In the embodiment of the speed reducer, each speed reducing means 1, 2, 3 is connected to a wheel Bb1, "links Aa1, Aa2, Aa3 rotatably supported around support shafts Pp1, p2, p3 provided on the door". Bb2, Bb3 are installed.

When the wheels Bb1, Bb2, Bb3 move along the sliding surface KK and rotate in the direction of arrow D in the figure,
The pulling springs Vv1, Vv2, and Vv3 are stretched to resist the “force of the drive unit closing the door”. The links Aa1, Aa2, and Aa3 are urged in the direction opposite to the arrow D in the figure by the pulling springs Vv1, Vv2, and Vv3, and are locked by a contact G (not shown) in a state substantially perpendicular to the door surface. Each of the speed reducing means 1, 2, and 3 resists the "force that the drive unit closes the door" when the wheels Bb1, Bb2, and Bb3 come into contact with the sliding surface KK, but the links Aa1, Aa2, and Aa3 are connected to the door surface. As it becomes parallel to the door surface from a substantially perpendicular state, it will not resist.
In FIG. 3A, only the wheel Bb1 presses the sliding surface KK to press the door D against the door stop Gd90, and the door stops when fully opened. When the door is closed from the fully open position, the wheel Bb1 comes into contact with the sliding surface KK and the speed reduction means 1 functions, and the speed reduction means 2 and 3 do not function. When the door is closed, the wheel Bb
2 comes into contact with the sliding surface KK and the speed reduction means 2 functions, and the speed reduction means 1 and 3 do not work.
In this manner, the wheels Bb1, Bb2, and Bb3 are sequentially brought into contact with the sliding surface KK, and the speed reducing means 1, 2, and 3 are sequentially operated. The range in which the decelerating means 1, 2, and 3 function is limited, and the form of resisting the "force that the drive unit closes the door" varies depending on the opening degree of the closing, and the rotation of the door when the latch contacts The speed and the magnitude of the “force acting on the door” are substantially constant without differing depending on the closing start opening.

In FIG. 3 (b), the link Aa2 is substantially parallel to the door surface and the resistance of the speed reduction means 2 is reduced. However, the resistance of the speed reduction means 2 is equivalent to the "force to dent the latch" When the “force for closing the door by the drive unit” is more than that, as the resistance of the speed reduction means 2 decreases, the “force acting on the door” increases and reaches the “force for recessing the latch”. In this case, “
There is no need to change the “force at which the drive closes the door”. When the "contact force of the drive part closes the door" is less than the "force to dent the latch" at the time of latch contact, the door will stop, but the drive part attached to the inner surface of the door will move without stopping in the "switching range" Continue to close the door.
The switchgear of FIG. 3 has a “passage of the wheel B continuous from the vicinity of the pivot axis O” as in the switchgear of FIGS. 1 and 2, but the sliding surface K of the path of FIG. The shaft is rotatably supported and is urged to rotate in the direction indicated by the arrow C in the figure by the pulling spring VV. The wheel B is mounted on a rotation shaft Ib of a wheel provided at the distal end portion of the link A, and the link A is attached to the distal end portion of the “rotary body J that is urged to rotate in the direction of the arrow A in the figure about the fixed support shaft Sw”. It is connected to a connecting shaft P provided. A bending force acts on the link A in FIG. 1, a compressive force acts on the link A in FIG. 2, and a tensile force acts on the link A in FIG.

The rotating mechanism around the rotating body J in FIG. 3 includes “(A) rotating means”, “(I) rotating means”, and “switching means”, and a space between the connecting shaft P and the fixed support shaft Sww. In this structure, the “continuous body in which the tension spring V and the link AA are connected by the connecting shaft Sa” is connected.
The side surface of the link AA around the connecting shaft PP moves along the fixed support shaft Sw. When the link AA and the fixed support shaft Sw come into contact with each other as shown in FIG. The acting force distance Lsw between the core wire Zv is small, and the smaller the distance between the fixed support shaft Sw and the connecting shaft Sa in the “(A) range”, the “around the fixed support shaft Sw acting on the rotating body J”. Rotational moment Mj "is small, and when the distance is zero, no force acts on the rotating body J in the" range (A) ".
As shown in FIG. 3 (c), the acting force distance Lsw becomes large when the vehicle is separated. As the acting force distance Lo increases, the rotational moment Mj increases. The movement of the pulling spring V away from the fixed support shaft Sw is interlocked with the rotation of the rotating body J, and the rotation of the rotating body J is accompanied by an increase in force. However"
While the "force acting on the door" develops, the door hardly rotates. The rotation mechanism around the fixed support shaft Sw is accompanied by the rotation of the rotating body J, but the rotation mechanism around the pivot axis O is not accompanied by the rotation of the door D.

As shown in FIG. 3A, the wheel B stays at the base end portion Ko of the sliding surface K in the “range (A)”.
“The acting force distance Lo between the pivot axis O and the acting line of the pressing force Fb” is small. As shown in FIG. 3B, in the “switching range”, the base end portion K of the sliding surface K in which the wheel B is substantially parallel to the “closed door surface D0”.
Move from o toward the end Ke. The wheel B starts to move when the “intersection angle Θka between the axis A of the link A and the sliding surface K” becomes an obtuse angle, and stops when the angle Θka is a right angle. When the compressive force acts on the link A as shown in FIG. 2, the wheel B does not stop during the movement.
Although the rotation bias in the direction indicated by the arrow C in the drawing by the tension spring VV becomes weaker as the wheel B moves, the “force for closing the door” stored in the tension spring V increases. When the sliding surface K is rotatably attached, even if the door stops, if the wheel B makes the crossing angle Θa an obtuse angle, the movement starts and the closing device continues to operate. As shown in FIG. 3C, when the wheel B reaches the terminal portion Ke of the sliding surface K, the acting force distance Lo becomes large and seals the door.

The door of the present invention requires a preparatory work for removing the inertial force of the door at the time of sealing so that the sealing work is the same in any case.
There is no vertical movement of the center of gravity in the rotational movement of the door whose rotation axis is vertical, and the door rotates with a force slightly exceeding the “maximum static frictional force around the pivot axis O”. To ensure that the door does not stay wherever you open the door and release your hand,
A force slightly exceeding the maximum static frictional force around the pivot axis O must be working. However, the door will rotate if it slightly exceeds the rotational resistance, and the excess force will be a component that accelerates the door. As long as it continues to operate even with a slight force, the accelerated door is further accelerated and a large inertial force is attached to the door just before closing. Since the inertial force is proportional to the square of the speed, the inertial force is extremely increased only when the closing speed is slightly increased, and is extremely decreased only slightly. If the magnitude of the resistance against this is not extremely large or extremely small, either the case where it does not work at all or the case where the door is stopped due to being too effective. A certain amount of resistance cannot handle a wide range of inertial forces.

4 to 6 are not intended to eliminate the grown inertial force with the resistance provided at one place near the “switching range”, but before the inertial force grows over a wide range of “(A) range”. It is to be resolved at the time of occurrence. FIG. 4 controls the magnitude of the “force acting on the door”. Instead of means for reducing the “driving force acting in the closing direction” by the force in the opposite direction such as resistance, the action line is moved. "Force acting on the door" by changing the acting force distance Lo
Can be changed freely. 5 and 6 do not control the magnitude of the “force acting on the door” but suppress the acceleration of the link device. FIG. 5 shows that by applying resistance,
In FIG. 6, the movement speed of the link device is delayed by changing the door inertia force to the braking force. 5 and 6 include a rotation means and a means for preventing rotation (hereinafter referred to as rotation prevention means), and the rotation prevention means is a means for reducing the “force acting on the door” in any case. Will never stop.
4 to 6 are the same in that the door inertia force is removed before the latch contact,
It explains that the sealing work is the same regardless of the "force acting on the door". In FIG. 4, the acceleration of the door is made as small as possible by making the magnitude of the “force acting on the door” as small as possible. 5 and 6, “(A) range” and “(
There is no boundary to “range”, and the magnitude of “force acting on the door” gradually increases from the middle of rotation, but the “(range)” suppresses acceleration and keeps the door inertia force small. Therefore, even if the size of the “force acting on the door” does not change when the latch abuts, the “force to dent the latch”
If it is good.

FIG. 4 is an embodiment for controlling the line of action of “the force Fb at which the wheel presses the sliding surface” as in FIG. 1, and the sliding surface around each of the pair of rotating shafts O and C provided on the door frame W. A cam body (hereinafter referred to as a sliding surface K) provided with K and a link A are rotatably supported, and a wheel B is mounted on a rotating shaft Ib of a wheel provided at the tip of the link A. By moving along the sliding surface K,
The door frame W and the sliding surface K are rotation mechanisms that rotate relative to a common rotation axis O. If the door frame W of FIG. 4 is considered as the door D of FIG. 1, it is the rotation mechanism of the same structure. The door frame W in FIG. 4 is a link having rotation axes O and C and is on the blank surface of FIG.
In FIG. 4, the door frame W and the sliding surface K are two open / close bodies that rotate relatively. When the two open / close bodies are compared to a door, either the door frame W or the sliding surface K is a door. The connecting shaft C is attached to the door frame and the sliding surface K is attached to the door, and the connecting shaft C is attached to the door and the sliding surface K is attached to the door frame. Even if the frame is replaced, it means that it is the same rotation mechanism. For this reason, the embodiment in which the drive unit of the switchgear of the present invention is attached to the door means that the embodiment is also attached to the door frame.

While the wheel B moves along the sliding surface K, the wheel B revolves in the direction of arrow B in the figure and the sliding surface K rotates in the direction of arrow A in the figure, “the pressing force Fb and the pivot O The distance Lf "between the springs V and the force of the spring V decreases, but the" distance Ls between the spring axis Zv and the pivot O "is adjusted according to the shape of the sliding surface Ko to keep the pressing force Fb constant. Can be made.
One end of the tension spring V is attached to the “support shaft Sk provided on the sliding surface K” and the other end is attached to the support shaft Swv provided on the door frame W, and the intermediate portion contacts along the sliding surface KK. As the sliding surface K rotates in the direction of arrow A in the figure, the pulling spring V is separated from the sliding surface KK, and the “distance Ls between the spring axis Zv and the pivot O” decreases, thereby reducing the wheel. Even if B approaches the base end portion Ko of the sliding surface K, the pressing force Fb is not increased.
By controlling the “distance Lc between the line of action of the pressing force Fb and the rotation axis C”, the “rotation axis C
The rotational moment Mc "acting around the head can be freely changed.
With b constant, as shown in FIG. 4A, “the line of action of the force Fb that the wheel B presses the sliding surface K”
When the distance Lc between the shaft and the connection axis C is always constant, the “rotational moment Mc acting around the rotation axis C” can be constant. The shape of the sliding surface K according to the drawing shown in FIG. 4C always makes the “distance Lc between the line of action of the pressing force Fb and the connecting shaft C” constant. The line of action of the pressing force Fb is always in contact with the “circle Rc about the rotation axis C”.

A solid line and a broken line shown in FIG. 4A are state diagrams when the opening degree of the link A is 60 degrees and 90 degrees, respectively, and are operation explanatory plan views of “range (A)”. Kee at the end of the sliding surface K is a sliding surface that reverses the urging direction when the link A is fully opened, and is for maintaining a stationary state when the link A is fully opened.
Unlike in the case of FIG. 1, in the case of FIG. 4, the wheel B moves to the end portion Ke of the sliding surface K as the door closes.
Moves toward the base end Ko, and moves large in “range (A)” and small in “range (I)”. However, the sliding surface K is small in the “(A) range” and is greatly rotated in the “(A) range” with the pivot O as the axis. In the case of FIG. 1, the wheel presses the sliding surface to rotate the door, but in the case of FIG. 4, when the link A is the door D, the sliding surface presses the wheel to rotate the door. In the case of FIG. 1, the wheel presses the sliding surface to rotate the door, but FIG. 4 and FIG. 1 are the same in that the action line of the pressing force Fb moves greatly in the “switching range”.
FIG. 4 shows a rotating mechanism that moves the wheel B in the circumferential direction with a small force while preserving the large force of the spring in the radial direction of the “circular motion about the rotation axis C” of the wheel B. Demonstrate. The link A is a rigid body that can move with a small force while supporting a large force with which the sliding surface K presses the wheel B, and can store a large force in the spring while opening with a small force when the door is opened.

The sliding surface K in FIG. 4 has a shape in which the curvature gradually increases as it approaches the base end portion Ko of the sliding surface K, and the moving speed of the wheel B becomes slower than the constant rotational speed of the door, but the sliding surface K The history of the “force acting on the door” can be designed freely according to the shape of the moving surface K. The curvature is increased at the base end portion Ko of the sliding surface K to decelerate before closing, and the curvature is reduced to be large when sealed. Force can be applied. In this way, the sliding surface K in FIG. 4 has the acting force while the action line of the pressing force Fb rotates greatly in the “(A) rotating means” that keeps the acting force distance Lo small and the small “switching range”. When the distance Lo is increased, the “switching means” and the action point move in the “radial direction of the circular motion of the link A around the rotation axis C”, and the action line becomes the circumferential direction of the circular motion. “(I) rotating means” that converts a small force for moving the point in the radial direction into a large force in the circumferential direction is provided.

The sliding surface K in FIG. 4 is a lid of a trunk room of an automobile that rotates up and down around a horizontal rotation axis O, and the urging means around the pivot axis O is moved around the connection axis C to be provided on the vehicle body. With the support shaft C as the axis
Assume that the link A with the wheel B attached to the tip rotates, and the lid K shifts from the horizontal state as shown in FIG. 4A to the suspended state as shown in FIG. 4B. When “the rotational moment Mc acting around the connecting shaft C” is constant, “the force Fb that the wheel B presses the sliding surface K” is also constant, and as the lid K shifts from the horizontal state to the suspended state, the “force The distance Lf "between the line of action of Fb and the pivot axis O decreases. A constant weight acts on the center of gravity of the lid K, and the direction is always kept vertical. Since both the constant pressing force Fb and the constant line of action approach the pivot axis O, the moments around the pivot axis O can be balanced.
In particular, when the lid K is almost horizontal, the link A is almost vertical, and the lid A supports the weight of the lid K in the axial direction of the link A, and the lid is applied even if the rotational force Mc acting on the connection axis C is small. K moves up and down. In the range where the lid K is close to the suspended state, the “balance of moments around the pivot axis O” is not maintained, but the strength of the spring is changed or the distance between the acting line of the force Fb and the connecting axis C is changed. It can be adjusted by making the virtual circle elliptical or by changing the shape of the sliding surface K.
As described above, the rotation mechanism in FIG. 4 is also a rotation imparting unit that provides a substantially constant rotational force to the “link A rotating on the horizontal plane”, and continuously changes to the sliding surface K that rotates in the vertical plane. It is also a means for providing a rotational force and a means for moving a large weight with a small force.

In Patent Documents 10 and 11, since the urging means works in the direction of gravity and counters with the same force as the weight, a strong urging means is required. In the rotating mechanism shown in FIG. 4, when the lid K is almost horizontal, the biasing means works at right angles to the direction of gravity and does not support gravity, so that the lid can be raised and lowered with a small force. When the lid K is close to the suspended state, no force is required to rotate the lid, so that the lid K can be rotated with a small force, and can be improved by slightly adjusting as described above.
In Patent Document 9, the moving direction of the action point changes from the circumferential direction of the circular movement of the lid to the radial direction at the time of closing, a large spring force is applied in the circumferential direction, and a partial force of the large spring force is radially applied. The effect of the sealing force is different from the present application. A member that supports a large force is not a rigid body but a spring.
When the rotation mechanism of the present application supports the lid, one of the two opening / closing bodies K and W sharing the pivot axis O is the lid, and the wheel B is the circular motion of the link A while the link A supports the weight of the lid. The lid is moved up and down by moving with a small force in the radial direction. The link A that supports the weight of the lid has a characteristic of being a rigid body. The center of gravity of the lid moves horizontally with the top and bottom of the lid, and the magnitude of the pressing force Fb changes, but the “distance Lc between the line of action of the pressing force Fb and the connecting shaft C” changes. The shape of the sliding surface K corresponding to the moving load can be drawn by designing the “shape instead of the circle Rc with which the line of action of the pressing force Fb contacts”.

The pivot O is “a rotating body Jc that is rotatably supported around a rotation axis Sww provided on the door frame W”.
The pivot O is movably attached to the door frame W via the rotating body Jc.
The rotating body Jc swings between a position locked to G1 in the “(range)” and a position locked to G2 in the “(range)”.
FIG. 4B is an explanatory view of the operation immediately before closing, in which the wheel B is in the vicinity of the proximal end Ko of the sliding surface K and is substantially stopped, and the contact b between the wheel B and the sliding surface K is a spring. When crossing the axis Zv of
When the sliding surface K rotates about the wheel B and the direction of the line of action of the pressing force Fb rotates, the “distance Lc between the rotating shaft C” increases abruptly and the “around the rotating shaft C”. Working rotational moment Mc "
Increase The solid line and the broken line shown in FIG. 4B indicate the state after rotation and before rotation, respectively.

In FIG. 4C, points bi (i = 0, 1, 2,...) On a circle Rb centered on the rotation axis C.
) Equally. Point bi (i = 0, 1, 2,...) Is a point of contact between the sliding surface K and the wheel B that moves over time. 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 rotation axis C. Arc Ri (i = 0)
, 1, 2,... Are arcs with the above-mentioned contact ai as the center and a radius of aibi, around the contact portion of the cam body sliding surface K that is in time contact with the wheel B moving on the circle Rb. is there. However, circle Rb
When the upper points bi (i = 0, 1, 2,...) Are finely and equally divided, the arc Ri is a line segment that passes through the points bi and is orthogonal to the tangent line Ti.
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 intersection 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.
An arc passing through the point bi (i = 0, 1, 2,...) And centering on the rotation axis O is an arc Oi (i = 0).
, 1, 2,..., The intersection point with the arc Ri-1 (i = 0, 1, 2,.
i = 0, 1, 2,..., and the arc bi-1Ci is centered on the rotation axis O and the arc Ki-
When it is rotationally moved to 1 (i = 0, 1, 2,...), The arcs R0, R1, Rb2,. Sliding surface K0K1K2K3K4K5 is wheel B
It is the sliding surface K shown to Fig.4 (a) (b) when a contact with is b7. As the sliding surface K approaches the base end portion Ko, the curvature increases, and the moving distance of the wheel B decreases as the link A rotates.
(For details on making the distance between the line of action of the pressing force Fb and the rotation axis C constant, refer to Reference 4 FIGS. 1 to 28 and the description of the related specification.)

FIG. 5 explains that the “switching means” is not limited to the door D, and the link device can continue to move even if the wheel B stops. The door stops even if a resistance is applied in the range of “(Ai)”. In order not to remain, it will be described that even in the “range (A)”, when the movement of the wheel B is resisted, the door is decelerated without remaining stopped.
The sliding surface K of FIG. 5 is provided with a “passage of the wheel B moving away from the pivot axis O” as in the sliding surface K of FIG.
It is substantially parallel to the closed door surface D0 ". The closing device protrudes greatly forward from the “closed door surface D0”, but when the wall thickness for attaching the door is large and the door is mounted behind,
There are few parts protruding from the wall.
As in FIG. 1, the door frame W is provided with a sliding surface K, and the wheel B moves in the direction of arrow A in the drawing along the sliding surface K, so that the door D is shown with the pivot O as the axis. Closes and rotates in the direction of arrow b. A link A is rotatably supported around the connection shaft C, and a wheel B is mounted on a rotation shaft Ib of a wheel provided at the tip of the link A. The connection shaft C is provided on a “rotary body Jc that is rotatably supported around a support shaft Cj provided on the door” and is movably attached to the door D. A pressing spring U is interposed between the rotating body Jc and the door D. As in FIG. 3, the urging means is a “continuous body that connects the pulling spring V and the link AA with the connecting shaft Sa” between the “support shaft Sb provided on the link A” and the “support shaft Sj provided on the rotating body Jc”. It is a structure to connect.

FIG. 5A shows the operation of the link device according to the opening Θd of the door D. A circle Rcj is a locus of the support shaft Cj. The action line of the pressing force Fb does not stay at the base end Ko of the sliding surface K in the “(A) range” but gradually moves away from the pivot axis O and gradually increases the acting force distance Lo. Line and link A
The “intersection angle Θaf” with the axial center line Za is large except when sealed as shown in FIG. 5D, and the “rotational moment Mc acting around the connecting axis C” is converted into a small pressing force Fb. FIGS. 5 (b) to 5 (d) are diagrams for explaining the operation from the time of contact with the latch to the time of sealing. Is straight.
When the link A and the rotating body Jc are in a straight line at the time of latch contact shown in FIG.
k is the smallest, the intersection angle Θaf is the largest, and the door is decelerated. The force that moves wheel B is the smallest, and the door stops without denting the latch. The push spring U is in the most extended state,
As shown in FIG. 5C, when the wheel B begins to move in the returning direction, the angle Θak increases and the wheel B
Is easy to move, and the crossing angle Θaf is reduced, so that the push spring U is easily contracted. FIG. 5C shows a state in which the push spring U contracts without the latch being recessed.
The contact Gjc shown in FIG. 5 (c) adjusts the upper limit of the “intersection angle Θjd between the door surface and the axis Zjc of the rotating body Jc”. Before the time, the link A and the rotating body Jc can be aligned. In this case, the angle Θa at the time of latch contact
Since k increases and the crossing angle Θaf decreases, the wheel B is more easily moved and the latch is more easily recessed.
At the time of sealing shown in FIG. 5 (d), the wheel B moves substantially parallel to the “closed door surface D0”, and the sealing force Fb0 acts at a substantially right angle. When sealed, the angle Θak is the largest and the crossing angle Θaf is the smallest. In this way, even if there is no "force to dent the latch" and the force to rotate the door at the time of latch contact, the link device continues to move even if the door is stopped if there is a force to contract the push spring U, Acting force "
Grows to the power to seal the door.

Fig. 5 shows a link device with a link number of 4 and a sliding pair evenly connected. When the rotation of one connecting shaft is fixed and the number of links is set to 3, the movement is determined as one, but the rotation of one connecting shaft is fixed. If you release, exercise becomes free. If a restraining means that can be released not only on the rotation of any link of the link device but also on the movement of any of the connecting points works, a change in the form and movement of the link device is recognized when the restraint is released or restrained. Even if the door is stopped in a range where the door and the drive unit do not interlock as in the “switching range”, the link device continues to move, but the door restarts, but even in the interlocked range, the wheel B is resisted and stopped. The link device continues to move and the wheel B restarts.
As shown in FIGS. 5 (b) and 5 (c), even when the door is stopped at the time of latch contact, the position of the wheel B and the rotation of the links A and Jc are free, and the drive unit also when the door stops in the middle of rotation. Move freely. FIGS. 5E and 5F are explanatory views of the operation of the deceleration means during rotation, and show a state in which the link device can freely move when the movement of the wheel B is restricted.

5E and 5F, the contact point b between the wheel B and the sliding surface K is the same position, the door opening Θd and the connecting shaft C are different, and the amount of expansion and contraction of the push spring U is also different. The sliding surface Kk is urged by a pressing spring Uk in the direction of the arrow C in the drawing with the "support shaft Sk provided on the door frame W" as an axis, and presses the wheel BB mounted on the connecting shaft C to move the sliding surface Kk. Give resistance. In FIGS. 5 (e) and 5 (f), the biasing means AA and V shown in FIGS. 5 (a) to 5 (d) are not shown, but a force is applied to the door so as to start moving the stationary door anywhere. is doing.
FIG. 5 (e) shows a state in which the door is accelerated when the rotation speed of the door is small and the push spring Uk is contracted, and the link A, Jc is hardly moved and the push spring Uk is extended. FIG. 5 (f) shows a state in which the door is decelerated when the rotation speed of the door is large and the pushing spring Uk is extended, and the pushing spring Uk is contracted while the door hardly moves. When the door is accelerated, the deceleration means works effectively, and when the door is decelerated, it works invalid.
The speed reducing means in FIGS. 5 (e) and 5 (f) self-controls according to the magnitude of the door inertia force, and is a means for taking resistance in the "(A) range" where the door and the drive unit are interlocked. There is no such thing as stopping. 5 (e) and 5 (f) illustrate that any of the connecting shafts of the link device is constrained, and the same deceleration effect can be obtained no matter what the constraint is.

FIG. 6 is a plan view for explaining the operation of the speed reducer in which the door inertia force acts as “a force that resists the closing rotation of the door”, FIG. 6A is “the range of (A)”, and FIG. FIG. 6C shows a range from the time of latch contact to the time of sealing.
The rotating body J is rotatably supported around a fixed support shaft Sw provided on the door frame W, and is rotationally biased in the direction indicated by the arrow C by the torsion spring UV, so that a driving force Mv acts around the fixed support shaft Sw. . Link A
A connects one end to the connecting shaft P of the rotating body J and the other end connects to the rotating shaft Ib of the wheel provided at the tip of the link A. The link A is rotatably supported around a connection axis C provided on the door D, and the rotation of the link A in the direction opposite to the arrow D in the drawing is prevented by the contact Ga. Link A
A wheel B is mounted on a rotating shaft Ib of the wheel provided at the tip of the wheel.

In “range (A)” shown in FIG. 6A, the link A and the door D are relatively integrated, and the wheel rotation shaft Ib is fixed to the door D. The rotating body J pulls the rotation axis Ib of the wheel via the link AA in the direction of arrow A in the figure, and the door D rotates with the pivot O as the axis in the direction of arrow B in the figure. The wheel B moves circularly around the pivot O in a range where the door opening is large, and the point of action (the wheel rotation axis Ib) stops near the pivot O. In the small opening range, the point of action (wheel rotation axis Ib)
Moves along a sliding surface K1 provided on the door frame W, but moves substantially parallel to the door surface, and the action line direction is maintained in the substantially pivot O direction so that the acting force distance Lo is kept small. When the wheel B moves along the linear portion near the pivot axis O of the sliding surface K1, the hitting Ga is released and the link A is connected to the connecting shaft C.
Is rotated in the direction of arrow D in the figure, but the rotation is small.

When the wheel B moves along the arc portion of the sliding surface K1 just before the closing shown in FIG. 6B, the force that the link AA pulls the rotational axis Ib of the wheel is suppressed by the sliding surface K1. The door inertia force pulls the rotating shaft Ib of the wheel via the link A, and the wheel B stops the rotation of the door while moving along the arc portion of the sliding surface K1. Moreover, the driving force distance Lv is large in the “(A) range”, and the driving force
Mv is smallly transmitted to "the force that pulls the rotating shaft Ib of the wheel", and when the wheel B comes into contact with the arc portion of the sliding surface K1, the connecting shaft P is almost stopped and the drive unit is the door. The force acting on the door is small, and most of the force acting on the door is the door inertia force. When the wheel B moves along the arc portion of the sliding surface K1, the link A moves from the radial direction of the circular orbit (b) of the connecting shaft C to the tangential direction as the door D of the rotation of the door closes. “Power to stop the rotation of the door” increases. When the door tries to rotate, the wheel B moves in the tangential direction of the circular orbit (b) of the connecting shaft C and stops the rotation of the door without following the radial direction.
Thus, when the wheel B moves along the arc of the sliding surface K1 as the wheel B decelerates due to insufficient force just before closing, the door inertia force strongly presses the sliding surface K1 and decelerates. If a “means for newly applying resistance to the movement of a wheel” is taken immediately before closing, the force is insufficient and the time for the wheel B to stop and move on the arc portion of the sliding surface K1 is delayed. Further, when a damper is attached around the fixed support shaft Sw to resist the rotation of the rotating body J, the deceleration effect due to the inertial force appears more prominently.
In the present invention, when a resistor or a damper is attached, the resistance is not applied directly to the door to decelerate, but a resistance is applied to one of the operations of the drive unit that rotates greatly against a slight rotation of the door just before closing. It decelerates and does not require large resistances or dampers. Especially when the resistances and dampers function in the “switching range”, the door and the drive unit do not work together, so the rotation of the drive unit affects the rotation speed of the door. It is always possible to decelerate to a predetermined speed.

The force with which the wheel B presses the sliding surface K1 is the “force that stops the rotation of the door” due to the door inertia force, and the pressing force increases as the door inertia force increases and increases the movement of the wheel B and the rotation of the door. Braking. When the door inertia force disappears, the pressing force disappears and the movement of the wheel B and the rotation of the door are not braked. Thus, when the door is decelerated by the “braking force due to inertial force”, the door stops or decelerates when there is a door inertial force, and when the door stops or decelerates and the door inertial force is removed, the door starts moving again. Or accelerate. The door is slowed down without remaining stationary. Moreover, even if the door inertia force is large before the deceleration effect works, it can be dealt with, and the deceleration effect is not too effective or not effective at all.
When the door is decelerated and the inertial force disappears, the wheel B moves away from the sliding surface K1 along the “sliding surface K2 facing the sliding surface K1,” and the door is moved as shown in FIG. Rotate. . The force with which the wheel B presses the sliding surface K2 is a force that rotates the door and accelerates the door. When the door is accelerated and the inertial force is attached, the wheel B moves along the sliding surface K1 facing away from the sliding surface K2. The movement of the wheel B on the sliding surface K1 and the movement on the sliding surface K2 are alternately repeated, and acceleration and deceleration act alternately on the door.

When the wheel B reciprocates between the sliding surface K1 and the sliding surface K2, the sliding surface K1 and the sliding surface K2 will collide with the sliding surface K1 several times, but they are separated from the sliding surface K1 and the sliding surface K2. Every time the wheel is unloaded, the sliding surface K
However, if the sliding surface K1 and the sliding surface K2 are rotatable and urged by a spring (not shown), or the connecting shaft C is “the support shaft Cj of the door is provided. If the rotary spring J is movably attached to the door D via the rotary body Jc that is rotatably supported around it, and a pressing spring U is interposed between the rotary body Jc and the door D, the sliding surface K1 When reciprocating between the sliding surfaces K2, a spring (not shown) or a pressing spring U that attaches to the sliding surfaces K1 and K2 is caused to oscillate, and the countless number of collisions are not transmitted to the door, and the wheels are moved. The movement to the terminal portion Ke of the sliding surface K2 is delayed.
As shown in FIG. 6 (c), as the wheel approaches the terminal end Ke of the sliding surface K2, the axis line of the rotating body J
The driving force distance Lv is reduced in the direction in which Zj and the axial center line Zaa of the link AA overlap each other, and the driving force Mv is greatly transmitted to the “force that pulls the rotating shaft Ib of the wheel” and strongly presses the door against the door contact Gd. To do. When the axial center line Zaa of the link AA and the “force that pulls the rotating shaft Ib of the wheel” are shifted to a straight line, a small force acts in the circumferential direction in the circular motion of the connecting shaft P, and the radial force is large. Power works. Even if the large radial force is small, the so-called wedge effect is achieved.
The other is decomposed into a sealing force that acts in the axial direction of the link A. Further, the pressing force Fb and the axial center line Za of the link A shift to a straight line.

In the first place, the sealing mechanism of the present invention is a state in which the “pressing force Fb for sealing the door” and the axial core line Za of the link A supporting the same are arranged in a straight line, and both are formed on the “closed door surface D0”. By moving the action point Ib of the pressing force Fb parallel to the “closed door surface D0” in a state orthogonal to each other, the small force in the direction of movement of the action point is changed to a large force perpendicular to the direction of movement of the action point. It is a mechanism for conversion and a sealing mechanism in which the wedge effect works.
In the sealing mechanism of FIG. 6, the wedge is the wheel B, one of the sliding surfaces on both sides of the wedge is the sliding surface K2, and the other is the link A that is rotatably attached to the door D. The more the “axial axis Za of the link A that supports the pressing force Fb” is perpendicular to the “closed door surface D0”, the stronger force acts on the door D when sealed, and the link A resists when opened. The link A can be opened by rotating. However, the link A rotates as the axial center line Za of the link A is not perpendicular to the “closed door surface D0”, and as the link A is shorter and the rotation radius of the action point Ib is smaller. “Resistance of link A when opening” is small.
Assuming that the sliding surface KD (not shown) is fixed to the door D and the wedge wheel B enters between the sliding surface K2 fixed to the door frame W, the space between the sliding surface KD and the sliding surface K2 is assumed. The wedge wheel B cannot be pushed back by narrowing the space between the sliding surface KD and the sliding surface K2. Thus, if one of the sliding surfaces on both sides of the wedge is not movable, it cannot be expanded even if the space between the sliding surfaces on both sides is narrowed. The sealing mechanism in FIG. 6 is a link A that can rotate the “sliding surface KD assumed to be fixed to the door D”.

Even if the door inertia force is not removed at the time of latch contact, the opening / closing device of FIG. 7 is adapted to remove the door inertia force at the time of sealing. “(A) rotating means”, “switching range”, “
It is an open / close device that does not have to include the “rotating means”.
Even if the door is decelerated until it stops before the latch contact, if a strong force is applied during the slight rotation of the door from the latch contact until the door is fully closed, a large inertial force will be attached to the door. The impact sound of can not be ignored. On the contrary, even when the door rotates at high speed and comes into contact with the latch, if the door is decelerated until it is sealed, the impact sound at closing can be ignored. Whether the "force acting on the door" is less than or equal to the "force to dent the latch" before sealing,
If a force slightly exceeding the "force to indent the latch" is applied, the problem of the impact sound at the time of closing is solved. In addition, the opening / closing device as shown in FIG. 7 that decelerates while the latch is depressed increases the force before closing when the “force acting on the door” decreases before sealing and becomes “the force that dents the latch” when sealing. However, even when it becomes “the force to dent the latch” at the time of sealing, the impact sound at closing is the same regardless of the history of “force acting on the door” before sealing.
The measures applied to reduce the impact noise are more effective the closer to the end of the door rotation, and the measures applied before that are the most effective means applied at the end of the door rotation. Is to do. The opening / closing device of FIG. 7 is a device in which means applied before that are integrated into the sealing device, and the sealing device also has a rotating function.

In the “switching range” in FIGS. 1 to 6, the drive unit and the opening / closing unit are not or hardly interlocked with each other.
In the “range” and “(ii) range”, the driving unit and the opening / closing unit are interlocked, and the driving unit moves by the door inertia force at the same time as the opening / closing unit moves by the driving unit. When the drive unit moves due to the inertial force of the door, the opening / closing unit moves due to the door inertial force, and the opening / closing unit moves freely, eliminating the need for the drive unit to move the opening / closing unit. Because it expands and contracts, it follows the door without delay. In this case, the driving part and the opening / closing part do not interfere with each other, and the driving part is free without obstructing the movement of the opening / closing part.
In the door where the inertial force of the door disappears immediately before closing, the drive unit closes the door after the “switching range”. The door in which the inertial force of the door has not disappeared moves even if the drive unit is stopped in the “switching range”, so there is no “switching range”, and the door is closed regardless of the driving unit in the “(ii) range”. When the door is closed by the door inertia force, the range of the magnitude of the door inertia force is large, so the range of the door impact sound is also large. Therefore, a situation where the door is closed by the door inertia force must be avoided.
The opening / closing device of FIG. 7 does not move the opening / closing portion regardless of the driving portion when the opening / closing portion moves due to the inertial force of the door, but the movement of the opening / closing portion by the door inertial force in the entire range where the door is closed. And a means (hereinafter referred to as “sealing prevention means”) that prevents the airtight seal even when the latch is depressed while being accelerated by the inertial force of the door.

“Suddenly decelerate while the door is slightly rotated” is accompanied by an impact close to a collision, and if the sealing prevention means is also provided with a buffering means for mitigating the impact before being sealed, Even when the door is rotating at a high speed when the latch is recessed, the door is sealed without a severe impact when closed. Since the sealing device of FIG. 7 absorbs an impact with a spring, the sealing prevention means and the sealing work proceed simultaneously so that the spring does not rebound in the opening direction due to the restoring force of the spring.
The sealing device shown in FIG. 7 allows the link device to operate greatly while the door is slightly rotated so that the inertial force of the door disappears while the large operation proceeds slowly and is delayed.
The "switching means" also has a feature that the link device operates greatly because the action line moves or rotates greatly while the door is slightly rotated. However, the "switching means" also in the sealing device of FIG.
The "feature that operates greatly while the door is slightly rotated" is that the door operates without load and does not rotate, and the operation ends instantly regardless of the size of the operation. However, when the closed door is opened, the link device cannot be operated largely without rotating the door, and the closed door cannot be opened.
The sealing device of FIG. 7 is a device in which a sealing prevention means is added to the “switching means”, and solves the problem that the operation ends in a moment and the problem that the closed door cannot be opened.

The structure of FIG. 7 is the same as the structure of FIG. 2, and the door D and the door frame W are interchanged. 7, the sliding surface K in FIG. 2 is attached to the door, and the connecting shaft C in FIG. 2 is attached to the door frame W. The wheel B is mounted on a rotation shaft Ib of the wheel provided at the tip end of the link A, and the link A is the tip end portion of the “rotating body J urged to rotate in the direction of arrow A in the figure about the fixed support shaft Sw”. Are connected to a connecting shaft P. The connecting shaft P moves “on the circumference Rsw1 centered on the fixed support shaft Sw in the direction of arrow A in the figure, and the wheel B presses the sliding surface K. As a result, the door D rotates in the direction of arrow B in the figure. .
The sliding surface K is rotatably supported by a connecting shaft C provided on the door D, and is urged to rotate in the direction opposite to the arrow C in the figure by a pressing spring U. The rotation of the sliding surface K in the direction opposite to the arrow C in the figure is prevented by the engagement of the bottom surface of the sliding surface K and the door surface. The sliding surface K is rotatably supported around the connecting shaft C, and the connecting shaft C is provided on the “rotary body Jc rotatably supported around the supporting shaft Cj provided on the door D”.

The surface Kd of the sliding surface K facing the door surface is concave toward the door surface and moves along the “sliding surface Kw provided on the door frame W” immediately before closing, and slides on the sliding surface K. The contact bk with the surface Kw moves while approaching the connection axis C as the door closes. The wheel B moves along the “surface Kb that does not face the door surface of the sliding surface K”. However, as shown in FIG. The acting force distance Lo is small because it is stopped at the base end Ko. As shown in FIG. 7B, when the sliding surface Kd comes into contact with the sliding surface Kw just before closing, the point of action b of the pressing force Fb is “the connection axis C of the contact bk.
On the far side, the pressing force Fb urges the connecting shaft C away from the direction approaching the door frame W to stop the door. As described above, the sealing device of FIG. 7 includes sealing prevention means for stopping the door just before closing.
The wheel B starts to move when the “angle Θak between the axis A Za of the link A and the sliding surface K” becomes an obtuse angle, and the “switching means” starts when the angle Θak is a right angle. As shown in FIG.
In the “switching range”, when the sliding surface Kd comes into contact with the sliding surface Kw, the angle Θak is an obtuse angle and the wheel B is “
It moves toward the end portion Ke of the sliding surface K that is substantially parallel to the closed door surface D0 ". "Wheel B
The force action line Fb "that presses the sliding surface K moves away from the pivot axis O.

The sealing device shown in FIG. 7 allows the action line of the pressing force Fb to be pivoted with little or no rotation of the door D.
A sliding surface K that is far away from the center is provided. While the action point (the wheel rotation axis Ib) moves linearly in parallel with the “closed door surface D0”, the action line of the force Fb goes straight in the “radial direction of the door rotation” during sealing.
When the action point moves without work, the spring expands and contracts in an instant, and neither the movement of the action point nor the “switching means” takes time, and from “(A) rotating means” to “(I ) Rotating means "
The door will be further accelerated as it takes time to switch.
In FIG. 7, the “passage K where the action point Ib moves away from the center O of rotation” is rotatably supported, and the “linear trajectory of the action point Ib” is curved and ascending. Resistance is applied to the movement of the action point Ib. Further, the door is decelerated by “a work for storing the sealing force in the push spring U”. Both the sealing device of FIG. 7 and the “switching means” of the present invention apply the load to the movement of the action point Ib so that the action point Ib shifts with time.

Further, as shown in FIG. 7C, when the point of action b of the pressing force Fb moves to the “side closer to the connection axis C of the contact bk”, the rotating body Jc rotates about the connection axis Cj in the direction of arrow C in the figure. At the same time, the sliding surface K also rotates about the connecting shaft C in the direction indicated by the arrow C in the drawing to contract the push spring U. Wheel B is the starting end Ko of the sliding surface K
The crossing angle Θa approximates a right angle and the wheel B strongly presses the sliding surface K. However, when the crossing angle Θa greatly shifts to an obtuse angle, the wheel B hardly presses the sliding surface K. Although it passes at a stretch, the moving speed of the wheel B is reduced by the compression of the push spring U.
When the wheel B reaches the terminal portion Ke of the sliding surface K as shown in FIG. 7D, the “contact point b between the wheel B and the sliding surface K” passes over the rotation axis C of the sliding surface K and passes. Therefore, the sliding surface K rotates about the connecting shaft C in the direction indicated by the arrow C in the drawing to contract the push spring U. When the push spring U contracts, the “impact received by the door” is alleviated and the door inertia force is reduced. The “door rotating force” and the “resisting force” simultaneously act on the sliding surface K and prevent the door from being sealed until the pressing force Fb seals the door. In this way, the sliding surface K and the door D move in the closing direction while being sandwiched between the two forces.
Next, the rotation of the sliding surface K is blocked by the contact Gk, and the sliding surface K is in a fixed state of the door D. Further, the sliding surface Kd is separated from the sliding surface Kw, and all of the pressing force Fb is changed to a force for sealing the door. At this time, the contact Gj comes into contact with the link A so that the rotating body J and the link A are relatively integrated. The rotation radius of the action point Ib centered on the fixed support shaft Sw is reduced, and the lever principle is activated at the end of the rotation, so that the driving force Mv is largely converted into the pressing force Fb.

When the door is sealed, the push spring U contracts, “The force in the direction opposite to the direction of closing the door increases and the force that the drive unit seals the door is increased, but the force acting on the door at the time of sealing is the same. If the door is opened, the force in the opposite direction reduces the “force to open the door”. Thus, the resistance at the time of sealing by the push spring U does not increase “the force acting on the door when sealing” nor “the force necessary when opening the door”.
For this reason, the rotation of the sliding surface K at the time of sealing shown in FIG. 7D is not prevented by the contact Gk, and the pressing force Fb is applied to the door while the sliding surface Kd is not separated from the sliding surface Kw. Even if the door frame and the door frame are pressed at the same time, "the force acting on the door when sealing" is also "the force necessary when opening the door"
Does not increase.

FIG. 7 (e) is a state diagram when the wheel B that has reached the terminal end Ke starts to return in the process of opening the door, and shows that the opening degree of the door is larger than that in FIG. 7 (d). Since the sliding surface K is rotatable, the wheel B is easy to return when the door is opened, and “the range in which a very small force is applied in the range where the door is sealed” in the closing process is the range in which a large force is applied in the opening process. , Indicating that the door will not open and stay where it is released.
In FIG. 7, when the door is opened, the link device can move while the point of action Ib remains at the terminal portion Ke of the sliding surface K, and when the door is opened, the sliding surface Kb rotates and the wheel B descends. Go back on the slope. The action point Ib moves away from the connection axis C while circularly moving around the connection axis C.
Moreover, it approaches the pivot axis O while circularly moving around the pivot axis O.

The opening / closing apparatus of FIG. 8 includes three links of two opening / closing bodies and a spring sharing a rotation axis, and each of the two opening / closing bodies has a spring mounting shaft, and the two opening / closing bodies are relatively moved by the expansion and contraction of the spring. A rotating mechanism that rotates in the direction of the shaft, and one of the mounting shafts is provided at a position close to the rotating shaft, and the other mounting shaft is provided at a position far from the rotating shaft, thereby reducing the expansion and contraction of the spring accompanying the relative rotation of the two opening / closing bodies. 8 to reduce the relative rotation acceleration of the two open / close bodies, and the open / close device of FIG. 8 has a mounting shaft close to the rotating shaft swingably mounted so that the axis of the spring is constrained to a position close to the rotating shaft. Then, the restraint is released at a predetermined opening degree of the two opening / closing bodies and moved to a distant position, and the force acting on the two opening / closing bodies is 2
It is characterized in that it changes from small to large or from large to small with little or no relative rotation of the open / close body.
The opening / closing device of FIG. 8 has one attachment shaft of the tension spring V provided on the support shaft Sa of the door D in the vicinity of the pivot O, and the other attachment shaft provided on the fixed support shaft Sw of the door frame W near the pivot O. Expansion and contraction of the spring V causes the door D to close and rotate in the direction of the arrow B in the figure, and the support shaft Sa of the door D is between the restraint position near the pivot O and the restraint release position far from the pivot axis O. Attached so as to be able to swing, the pulling spring V is pivoted on the pulling spring V with a predetermined opening degree of the door crossing the connecting shaft C.
By swinging between a restraining position close to the position and a restraining release position far from the position, the rotational moment acting around the pivot axis O can be increased from small to large or large with little or no rotation of the door. A rotation mechanism characterized by turning to small is provided.

First, the operation of the link device shown in FIGS. 8A to 8D will be described.
The link A is urged by the pulling spring V so as to rotate in the direction opposite to the arrow A in the figure with the connection axis C as the axis. As shown in FIGS. Ga prevents rotation in the direction opposite to arrow A in the figure. As shown in FIG. 8C, in the “switching range”, the connecting shaft C crosses the axis Zv of the spring due to the closing rotation of the door D. As shown in FIG. The link A is separated from the hit Ga and rotates in the direction of arrow A in the figure.
The “sliding surface Ga provided on the door frame W” is a releasable restraining means that engages with the side surface of the link A in the “(A) range” and disengages in the “switching range”. “Range” constrains the rotation of the link A, keeps the support shaft Sa in the vicinity of the pivot O, and keeps the acting force distance Lo small.
Then, the restraint is released and the support shaft Sa is moved away from the vicinity of the pivot O to increase the acting force distance Lo. (Hereinafter, the link that engages and disengages from the restraining position, such as link A, will be referred to as a swing link.)
The continuous body AV of the swing link and the tension spring V in FIG. 8 is similar to the “continuum AV of the tension spring V and the link A” in FIGS. In this case, in the case of FIGS. 3 and 5, the support shaft Sa is greatly increased. It is attached in the vicinity, and the door is rotated in the “switching range”. In the case of FIG. 8, the support shaft Sa is attached to the far side of the pivot O, and the axial center line Za of the link A and the axial center line Zv of the spring are folded back. “Switching range” does not involve door rotation.
In FIG. 8A, “the contact point ba between the side surface of the link A and the sliding surface Ga” is biased in the direction in which the door opens and is farther from the pivot axis O than the spring support shaft Sa, and remains stationary when fully opened. I am doing so.

Even if the force for rotating the door in the “switching range” is zero, the force for rotating the link A in the direction of the arrow A in the figure gradually increases from the time when the connecting shaft C crosses the axis Zv of the spring. Link A
When rotating around the connecting shaft C, the amount of expansion and contraction of the spring increases as the rotation starts small. Since the rotational speed of the link A is proportional to the amount of expansion and contraction of the spring, it starts very slowly at the beginning of rotation. As the support shaft Sw on the fixed side of the spring is closer to the center of rotation of the link A, it rotates more slowly.
FIG. 8D shows a sealed state, and the distance Lo is increased even when the link A does not rotate greatly by the connection shaft C being separated from the pivot O. If the length of the link A and the length of the spring are increased and the support shaft of the spring approaches the connecting shaft C, the amount of expansion and contraction of the spring decreases when the link A rotates. Since the change in spring strength with the rotation of link A is small, link A hits G
Start moving slowly away from a. Since the strength of the spring is not related to the rotational speed of the link A, a strong spring is used to bring the “support shaft Sa on the side close to the pivot axis O of the spring” as close as possible to the pivot axis O. If the rotation of the link A at the time of closing is made small so that "" acts on the door small, the device becomes small at the time of closing, and the device at the time of closing can be accommodated small.

In the “switching range”, even if the door is stopped or continues to rotate with the inertial force of the door, the telescopic portions A and V continue to move regardless of the rotation of the door. This means that neither the opening degree of the door when the link A starts to rotate nor the opening degree of the door when the link A finishes rotating is slightly constant.
In the “range (ii)”, the expansion / contraction part becomes a four-bar rotation mechanism including two links of the tension spring V and the link A, and since one of the links is a spring, the tension spring V remains with the rotation of the opening / closing body stopped.
And link A can rotate. This means that the form of the link device is not constant with respect to a predetermined door opening. Depending on the door inertia force, the door operation may be delayed or overtaken by the drive unit.

Next, the switchgear shown in FIGS. 8E to 8H will be described. 8 (e) to 8 (h) are shown in FIG.
The operation explanatory plan view of the switchgear having a structure in which the link A shown in a) to (d) is equipped with the sealing wheel B and the sealing prevention wheel BB, and including the sealing means and the sealing prevention means. It is. The contact Ga attached to the side surface of the link A is a releasable restraining means that engages and disengages with the rotating body Jc. In the “range (A)” shown in FIG. Door contact Gd
On the far side, the contact Ga engages the rotating body Jc. In the “switching range” and “(i) range” shown in FIGS. 8F to 8H, the connecting shaft C is on the side closer to the door spring Gd of the pulling spring V, and the contact Ga is separated from the rotating body Jc. When link A rotates about connection shaft C in the direction of arrow A in the drawing and Ga is separated from rotating body Jc, wheel B and sliding surface K are engaged, and connection shaft C is pivoted about pivot axis O. Revolves in the direction of arrow B in the figure.
1 to 7, the wheel B and the sliding surface K are not engaged and disengaged, but FIG.
In the “switching range” shown in (h), the movement of the link device may be delayed or preceded by the door movement, and the rotation of the link A is completed before the wheel B and the sliding surface K are engaged. When the wheel B and the sliding surface K are engaged with each other, the rotation of the link A starts after the wheel B and the sliding surface K are engaged, and the door may be sealed without completing the rotation of the link A. In the former case, see FIG.
As shown in (f), between “the position b10 where the connecting shaft C crosses the axial center line Zv of the tension spring V and the wheel B and the sliding surface K engage” and the base end portion Ko of the sliding surface K This can be solved by extending the distance. In the latter case, the problem can be solved by providing "sealing prevention means for preventing the door from being sealed by the door inertia force, not by the drive unit" so that the door inertia force is not affected at the time of sealing.
The sealing prevention means stops the movement of the link device when the door inertia force does not completely disappear before sealing, and when there is the door inertia force, both the door and the drive part stop completely, and the door inertia force When it runs out, it starts moving again.

The opening / closing device shown in FIGS. 8 (e) to 8 (h) is “(A)
The latch male part Rd becomes female part Rw so that the door is sufficiently decelerated by closing with a weak spring force in the range of "the range", and at the beginning of the sealing operation, the door stops or is brought close to it due to insufficient force. In this case, the “force acting on the door” does not have a force to dent the latch.
As shown in FIG. 8 (f), the history of “force acting on the door” in “range (A)” varies depending on the position of the mounting shaft Sa of the spring revolving around the pivot O. As the mounting shaft Sa moves away from the pivot axis O, the acting force distance Lo increases and the “force acting on the door” increases. However, as the mounting position approaches the door surface as in the mounting shaft Saa, the “force acting on the door” increases. “It is large when fully open and small when fully closed. It starts to close quickly and decelerates as it closes. As the mounting position is further away from the door surface as with the mounting shaft Saaa, the “force acting on the door” is larger when fully opened and larger when fully closed. The former is adopted when it is better to start closing early like a toilet door, and the former is adopted when it is better to start closing late with a door passing by holding an object.
The shape of the sliding surface Ga shown in FIGS. 8E to 8H is such that the mounting shaft Sa is brought closer to the door surface before the closing dimension, and the action line of the force acting around the pivot O before the closing dimension is expressed as the pivot O. By making the direction, the “force acting on the door” is brought close to zero.

As shown in FIG. 8 (f), the inertial force of the door is extinguished by slowing down the movement speed of the drive unit and delaying the switching work time at the time of latch contact.
The “revolving track about the pivot axis O of the wheel B” is substantially parallel to the base end portion Ko of the sliding surface K, and “
It is substantially orthogonal to the “revolution trajectory having the connection axis C of the wheel B as an axis”. The wheel B receives a large resistance at the beginning of engagement with the entrance Ko of the sliding surface K, and the resistance decreases as the wheel B enters the inside of the sliding surface K. When the wheel B is at the entrance Ko of the sliding surface K, the door is decelerated. As the wheel B approaches the terminal portion Ke of the sliding surface K, a large sealing force is applied even if the spring force is small.
The sliding surface K that engages with and disengages from the wheel B of the present invention gradually increases in angle Θak as the wheel B enters the inside from the entrance, and is difficult to move even if the force in the moving direction of the wheel B is large at the entrance. As the vehicle enters the vehicle, even if the force in the moving direction of the wheel B is small, it becomes easy to move. At the beginning of the “switching range”, the wheel B decelerates even if the spring bias is large by moving along the “sloped sliding surface K even if the distance is short”, and the end of the “switching range”. Further, the wheel B is moved over a long distance along the sliding surface K having a gentle slope, so that the door is sealed even if the biasing force of the spring is small.

When the wheel B moves up the slope of the sliding surface K in the “switching range”, the “slight force acting in the moving direction of the wheel B” is converted into “a large force acting in the direction perpendicular to the moving direction” as the upward slope is gentle. However, the moving speed of a spring-operated door becomes faster as the ascending slope becomes slower.Normal speed reducing means keeps a constant speed, so it slows down when converting a weak force into a strong force. Even though the “movement distance of the wheel B for slightly rotating the wheel B” is long, it passes through in an instant. To slow down the moving speed of the wheel B, even if the moving distance is short, the ascending slope is steep and the wheel B is moved with a weak force as much as possible so that the force for moving the wheel B is insufficient. is required. Thus, the speed reduction means for providing resistance at the entrance of the sliding surface K and causing a shortage of force at the beginning of the “(range)” and delaying the movement of the wheel B brakes the movement of the telescopic portion. Therefore, it is executed reliably without being affected by the inertial force of the door, and the deceleration means does not stop the door halfway.

In the case of FIGS. 8A to 8D, since the rotation of the link A and the rotation of the door are not interlocked in the “switching range”, the link A can be rotated about the connection axis C even if the rotation of the door is stopped. The door is sealed even if the spring force does not cause the door to rotate. In the case of FIGS. 8F to 8H, when the wheel B moves along the sliding surface K, the rotation of the link A and the rotation of the door are slightly interlocked. Even if the force of the spring does not cause the force to rotate the door without stopping, if there is a “force that moves the sealing wheel B along the sliding surface K to the end portion Ke of the sliding surface K”, the wheel B
Presses the sliding surface K, and the connection shaft C revolves around the pivot O. As shown in FIG. 8 (h), there are two action lines of “force acting on the door” in “range (ii)”, and one is the axis Zv of the spring, which is far away from the pivot axis O. The other is a line of action of the force Fb that the wheel B presses the sliding surface K, and suddenly appears at a position far from the pivot axis O. As the sliding surface K is provided farther away from the pivot axis O, the distance between the line of action of the pressing force Fb and the pivot axis O becomes larger and the door is more tightly sealed.
Further, the sealing preventing wheel BB moves around the contact Gw provided on the door frame W, so that the door is not sealed unless the link A rotates about the connecting shaft C.

When the door is stopped just before closing or the door is sufficiently decelerated, the link A starts to rotate around the connecting shaft C and the wheel B moves along the sliding surface K. Revolving around the connection axis C with a very slight distance without contacting the contact Gw attached to the frame W. If the wheel B moves along the sliding surface K while the door does not decelerate and closes without being stopped just before closing, the wheel BB hits and collides with Gw. Wheel BB hits Gw
When the rotational speed of the door at the time of collision is relatively low, the link A continues to rotate, and when it is large, the rotation stops and the rotation of the door stops.
In the “switching range”, when the speed at which the door rotates due to the inertial force of the door is faster than the “speed at which the door closes due to the rotation of the link A”, the link A shown in FIG. The part Rd comes into contact with the female part Rw and the latch is recessed, but the wheel BB hits and presses Gw so that neither the drive part nor the door rotates, and the door D has the latch male part Rd at the female part Rw. Stop at the position until it fits.

As shown in FIG. 8 (e), the rotation axis Ibb of the wheel BB moves on the "circular orbit Rbb centered on the pivot O" and passes through a position farther from the pivot O than Gw. If wheel BB hits and engages Gw without any “rotation of link A in the direction of arrow A”, “wheel B
"The force that B hits and presses Gw" rotates the link A in the direction opposite to the arrow A in the figure, and the link A
Stops while being engaged with the door while being engaged with Ga. As shown in FIG. 8G, while the door rotates at a high speed and the latch is recessed, the smaller the “rotation of the link A in the direction of the arrow a in the figure”, the more the drive unit and the door are prevented from rotating. While the state where the wheel BB hits and presses the Gw continues, the inertial force of the door disappears and the drive unit and the door rotate again. As shown in FIG. 8 (h), at the time of sealing, the wheel BB is separated from Gw and all of the force Fb that the wheel B presses the sliding surface K acts on the door.
When door inertia force participates in sealing, the magnitude of the door inertia force is not constant, so the impact sound at closing is not constant, but the structure where the link A has both the sealing wheel B and the sealing prevention wheel BB is "
The door is closed by the rotation of the link A while preventing the “rotation of the door by the door inertia force” from preceding the “rotation of the door by the rotation of the link A”, and the door inertia force does not affect the sealing.

As in the case of FIG. 1, the rotation mechanism of FIG.
When the spring U is inserted between the drive rotary shaft C and the door D, the rotary body Jc is provided so as to be movably attached to the door D, and is shown in FIG. Thus, even when the latch male part Rd is in contact with the sliding surface part Rww and the door is stopped, the force for contracting the spring U can be obtained even if “(a) rotating means” does not have the force to rotate the door. If there is, the link A starts to rotate only when there is a force that the connecting shaft C crosses the spring axis Zv, and the “switching means” operates. The distance Lv "between the connecting shaft C and the spring axis Zv" changes greatly, the rotational force Mc acting around the drive shaft C increases, and the force of "(i) rotating means" gradually increases. The spring U expands and contracts, and the “force stored in the spring U” reaches the force that seals the door. At the same time when the “force stored in the spring U” reaches the force for sealing the door, the latch begins to be depressed by the restoring force of the spring U. At this time, the rotation of the link A hardly occurs and the spring U is largely restored. When the spring U is restored, the door that has been stopped starts to rotate again and is sealed.

As shown in FIG. 8 (f), when the latch male part Rd comes into contact with the sliding surface part Rww of the female part Rw and begins to be depressed, the “largest force” is necessary, and thereafter, as shown in FIG. 8 (g). When the latch moves along the sliding surface portion Rww while being depressed, and the latch pops out again and fits into the door frame W as shown in FIG. 8 (h), little force is required. If the “maximum force required when the latch is recessed” continues to work in the process shown in FIGS. 8F to 8H, the force resisting the maximum force until the latch is sealed after the latch is recessed is In addition, the door accelerates while moving along the sliding surface portion Rww while the latch is recessed. Even when the “switching means” is activated after the door stops, a loud impact sound is generated when the door is sealed.
When a measure is taken to stop the rotation of the link A around the connection axis C at the moment when the latch is depressed, the latch male portion Rd is depressed as shown in FIG. 8 (g), and as shown in FIG. 8 (h). The rotation of the door until the latch male part Rd jumps out is driven by “the force that the elastic spring U restores”. Latch male part Rd
When the springs pop out and fit into the female part Rw, the door rotates and the spring U loosens, the “force acting on the door” decreases, and the force acting on the “closed door” also becomes very small. The force required to open the door is also very small, making the door feel lighter. Moreover, since an excessive force more than necessary does not work at the time of closing, the impact sound is reduced.

As shown in FIG. 8 (h), when sealed, the wheel B moves to the sliding surface K along the sliding surface Kw, and the wheel B and the wheel BB move parallel to the “closed door surface D0”. It will be restrained so as to prevent the rotation of the door. As in FIG. 7, when the wheel B moves along a groove substantially parallel to the “closed door surface D0” just before closing, the movement of the wheel B toward the “closed door surface D0” is prevented. The door will stop rotating.
The connecting shaft C is sandwiched between two forces of “the force Fb that the wheel B presses the sliding surface K” and “the force that the wheel BB presses the sliding surface Kw”. The link A rotates with the surrounding revolutions substantially stopped. Since the revolution of the connecting shaft C and the rotation of the door D are linked via a spring U, the revolution locking of the connecting shaft C and the locking of the rotation of the door D substantially coincide with each other, and the sealing prevention means is a door. The door is braked immediately before sealing, gradually approaching to the door stop Gd while keeping the “position until reaching the door stop”. The sealing mechanism shown in FIG. 8 (h) is means for sandwiching the door with a sealing force and a force for preventing the sealing against the sealing mechanism (hereinafter referred to as a sandwiching means).
Means. When the predetermined position is “a position where the latch male part Rd fits into the female part Rw and reaches the door stop”, the sandwiching means minimizes the impact sound.

In the case of FIG. 8 as well, as described with reference to FIG. 6, the “small force acting in the moving direction of the wheel B” is broken down into a force for bringing the door D into close contact with the door stop Gd and a force for the wheel pressing the sliding surface. The door is sealed by the effect.
The closer to the state where the two forces to be disassembled are arranged in a straight line, the magnitude of the two forces increases, but it becomes a resistance when opening the closed door. The wheel B tries to move in the “perpendicular direction to the closed door surface D0” according to the movement of opening the door, but the sliding surface K or the rotating shaft C prevents this.
“The door closed by the wedge effect” has the disadvantage that it is harder to open as the “small force in the moving direction” of the wheel is converted to “the force in the direction perpendicular to the moving direction”, and when opening a closed door When the link A rotates, the door can be opened. The link A revolves while rotating around the pivot O, but the link A rotates, so that the wheel B moves in a direction perpendicular to the “closed door surface D0” with the slight rotation of the door. Door surface D0 "
And move in a parallel direction. As link A rotates, link A becomes easier to rotate.
The position “(ii) rotating means” returns to the position “(A) rotating means”.
In the process of closing the door, the direction of the “force to close the door” approaches the direction perpendicular to the “closed door surface D0”, and the direction of the “force that the wheel presses the sliding surface” is the sliding surface. The closer to the direction perpendicular to K, the weaker force is converted into a stronger force. However, the door cannot be opened after passing through the direction perpendicular to the “closed door surface D0” or the sliding surface K. So
It is desirable to approach the perpendicular direction as much as possible without passing through the perpendicular direction.

8 works within a very short time during the movement along the door frame W while the latch is depressed, reducing the closing speed of the door. However, it is merely that the collision at the time of sealing occurred before the sealing. In order not to cause a rapid decrease in speed, the door closing speed when the latch abuts against the door frame W must be small and sufficiently slowed down.
When the latch abuts against the door frame W, the door is not stationary, but when the door moves, the latch collides with the door frame W, and the weight of the door works as an impact load. The inertial force reduces the “force required when the latch abuts against the door frame W and is recessed”.
A closed door has a “sealing force”, and when opening the closed door, it is necessary to apply a force of the same magnitude as the “door sealing force” in the opposite direction. In order to reduce the force required to open a closed door as much as possible, the “force to seal the door” must be as small as possible. For this purpose, when the latch abuts against the door frame W, the door is not stationary, but the inertial force participates in the sealing operation with the door moving to a certain degree. It is better to reduce the “force required sometimes”. For this reason, it is desirable that the closing speed of the door at the time of latch contact is large enough that the above-described sealing means does not cause a collision.
When the door is moving just before closing and the wheel BB revolves around the connection axis C without contacting the contact Gw attached to the door frame W, the latch becomes a sufficient speed reduction means, and the latch is recessed. The inertial force is reduced by, and the door is decelerated by the concave depression of the latch.

The force of the spring for sealing is reduced by the amount of inertia force participating in the sealing work, but the wheel BB hits Gw just before closing and decelerates by contacting Gw, but if there is no inertial force, the door stops. It means that. In the closing process, when the latch passes the position where it abuts against the door frame W, the door inertia force is attached, but when the "closed door" is opened and the latch is released from the door at the abutting position on the door frame W The door does not reach the sealing force as much as the inertia force of the door is not attached, and the door remains stopped and does not close. However, as explained in Fig. 1, the position just before closing in the closing process is the position where "(i) rotating means" works in the process of opening the door, and the door will stop regardless of where the hand is released. The seal will not be closed.
As shown in FIG. 8 (f), in the closing process, just before the closing, the rotating body Jc and the link A are opened from the closed state, and the “wheel B in a state separated from the sliding surface K” is the sliding surface K. As shown in FIG. 8 (h), the rotating body Jc and the link A are closed from the opened state according to the opening Θds of the door that changes to “wheel B in contact with the sliding surface K”. The opening Θdo of the door that is separated from the sliding surface K is large, and “(i) rotating means” works in the range below the opening Θdo of the door.

When the door is fully opened and the hand is released, the inertial force is used for the sealing operation. When the door is opened a little and the hand is released, the strong “(i) rotating means” exceeds the inertial force, and the door does not remain stopped even though the inertial force is closed and starts to close. In addition, when the door is fully opened and the hand is released, the speed reduction means operates before sealing. However, when the door is opened slightly and the hand is released, the speed reduction means does not operate.
As described above, when one of the links of the four-bar rotation mechanism is replaced with a spring, the degree of freedom of the link device is increased, and a difference in the form of the link device is recognized when the door is closed and opened.

The opening / closing device of FIG. 9 is a rotation device in which a driving force acts at a position close to the pivot O and a position near the pivot O, and a sealing device in which a driving force acts at a position far from the pivot O and far from the pivot O. The operation of rotating the door with a predetermined opening of the door as a boundary is inherited from the rotating device to the sealing device.
As in the case of the opening / closing device of FIG. 8, the three opening / closing bodies D, W sharing the rotation axis O and the three links of the spring V are provided, and one of the attachment shafts of the spring V is located close to the rotation axis O 8 is a link device provided at a position far from the rotation shaft. Unlike the opening and closing device in FIG. 8, the attachment shaft at a position far from the rotation shaft is mounted so as to be swingable. When the “fulcrum Sa of the spring provided at a close position” moves, the “distance Lv between the line of action Zv of the spring force and the pivot O” greatly changes, but “from the pivot O as in the embodiment of FIG. When the other support shaft of the spring provided at a distant position moves, there is almost no change in the “distance Lv between the spring force action line Zv and the pivot O” due to the movement of the spring fulcrum.
However, in FIGS. 2 and 8, the connecting shaft C is located far from the pivot axis O, and the link supported by the connecting shaft C rotates significantly in the “(range)”. This large rotation is observed at a position far from the pivot axis O. As in the case of the opening / closing device of FIG.

One support shaft Sw of the spring is provided on the door frame W, and the other support shaft Sa is connected to the door D with the link A and the rotating body J.
The fixed support shaft Sw is located close to the pivot O and the support shaft Sa is located far away.
The link A has a connecting shaft C in the middle and a sealing wheel B and a spring support shaft Sa at one end and a sealing prevention wheel BB at the other end. The wheel B is mounted on the rotating shaft Ib, the wheel BB is mounted on the rotating shaft Ibb, the rotating body Jc is rotatably supported around the “support shaft Cj provided on the door”, and the connecting shaft C is movable to the door. Mounted. In FIG. 9A, the state of “(A) range” before the connecting axis C crosses the axial axis Zv of the spring is indicated by a broken line, and the state of “(A) range” after that is indicated by a solid line.
If the support shaft fixed to the door frame W by the spring support shaft is called a fixed support shaft, and the non-fixed support shaft is called a revolving support shaft, the pivot O and the fixed support shaft are connected as shown in FIG. The biasing direction of the spring changes with the straight line Tv as a boundary, and the change in the amount of expansion and contraction of the spring occurs when the revolution support shaft is on the side farther from the pivot O and the revolution support shaft is on the side closer to the pivot O. Smaller than Arc Ro is pivot A,
If the circular arc Rs is a circle centered on the fixed support shaft, the region between the circular arc Ro and the circular arc Rs indicates the amount of expansion and contraction of the spring. The rotation of the door in the direction indicated by the arrow B in FIG.
Thus, the link A is rotated in the direction of arrow A in the drawing by the tension spring V which is “(i) rotating means”. In the “(A) range”, the tension spring VV is shortened to rotate the door in the closing direction, and the tension spring V is lengthened to bias the door in the opening direction. In this way, by separating the spring engaged in the rotation work and the spring engaged in the sealing work, the magnitude of the force acting on the door can be designed to be unique in the rotation work and the sealing work, regardless of the acting force distance Lo. Since the size can be adjusted according to the strength of the spring, the device can be miniaturized by increasing the strength of the spring so that the operating point is close to the pivot axis O. In FIGS. 9B and 9C, illustration of the spring is omitted.

The support shaft close to the pivot O of the tension spring V is attached to the door frame W, and the support shaft far from the pivot D is attached to the door D.
A support shaft close to the pivot O of V is attached to the door D, and a support shaft far from the support shaft W is attached to the door frame W. Since the door D and the door frame W are two opening / closing bodies that share the pivot O and rotate relatively, both of them are pivot O
This is the same as closing the spring as an urging means. However, only the operation differs depending on the mounting position. Even if the door D and the door frame W are replaced in this manner, the connection mechanism attached to the door frame W is assumed if the door is fixed and the door frame rotates around the pivot O in FIG. It can be understood that the case where the link A with the wheel B mounted around the axis C rotates and the sliding surfaces K1 to K3 are attached to the door is the same as the embodiment shown in FIG. For this reason, in the other embodiments of the present invention, even if the door D and the door frame W are replaced, the same rotation mechanism is used. This means that it may be attached to either the door D or the door frame W.

The rotation of the link A in the direction opposite to the arrow A in the drawing is blocked by the contact G1, and the rotating body Jc swings between the position locked by the contact G3 and the position locked by the contact G3. Move. As shown by the solid line in FIG. 9A, when the connection axis C crosses the axial center line Zv of the spring, the link A rotates about the connection axis C in the direction of arrow A in the figure. The wheel B is attached to the surface of the link A, and the wheel BB is attached to the back surface of the link A with the link A interposed therebetween, and the horizontal plane on which the link A operates is different. The sliding surface K1 is disengaged from the wheel B, and the sliding surfaces K2, K3 are disengaged from the wheel BB. The sliding surface K1 and the sliding surfaces K2, K3 are provided on the horizontal planes on opposite sides of the horizontal plane on which the link A operates.
FIG. 9B is a state diagram of the link device with the door opening degree being 15 degrees, 11 degrees, and 10 degrees, and shows the state before the closing dimension, before the latch contact, and at the beginning of the latch contact, respectively. The link A passes over the sliding surfaces K2 and K3 under the sliding surface K1 while the door opening is between 15 and 11 degrees. When the opening degree is between 11 degrees and 10 degrees, the link A rotates and moves on the sliding surface K2, and then moves on the sliding surface K3.
FIG. 9C is a state diagram of the link device in which the door opening degree is 10 degrees, 9 degrees, and 8 degrees, and shows a state at the beginning of the latch contact, after the latch contact, and immediately before the fully closed state. Wheel B is on the sliding surface K1, wheel B
B simultaneously moves on the sliding surface K3 and closes and rotates the door while preventing sealing. Connection axis C
Moves in the direction of the arrow B in the figure, and the rotating body Jc rotates in the direction of the arrow C in the figure to be integrated integrally with the door D and the door is fully closed.

When the wheel B moves along the sliding surface K1, the so-called wedge effect "small force acting in the moving direction of the wheel B" is along the force that the wheel B presses the sliding surface K1 and the axis of the link A. It is decomposed into a working axial force, and the latter is supported by a latch. The force supported by the latch gradually increases because the connection shaft C is substantially stopped when the wheel BB moves on the sliding surface K3, and the latch is eventually recessed.
FIG. 9 shows a “rotation mechanism in which the action point is shifted from a position close to the pivot axis O to a position far from the pivot axis O”, and “the force for rotating the door” in the “(range)” brings the fixed support shaft Sw closer to the pivot axis O. By approaching zero as much as possible, the “force to seal the door” in the “(range)” is increased by moving the sliding surface K away from the pivot O. The “rotation mechanism in which the action point shifts from a position close to the pivot axis O to a position far from the pivot axis O” can adjust the ratio of “the force for rotating the door” and “the force for sealing the door” between zero and infinity.

If the “line of force acting on the door” is brought as close as possible to the pivot O just before closing, and the “force acting on the door” disappears, the door decelerates just before closing. The door stops at a position where the “straight line Tv passing through the door pivot axis O and the mounting shaft Sw” and the spring axis Zv coincide with each other when the hand is fully opened and released. The tension spring VV has one support shaft Sa2 as the door D,
The other support shaft Sw2 is attached to the door frame W, and serves to bring the “opening degree of the door when the force acting on the door disappears” closer to a predetermined position where the “switching means” starts to operate.
Although the rotation of the door is large compared to the small operation of “(a) Rotating means”, it is difficult to adjust “the position where the door stops” to “the position where the latch abuts against the door frame”. , Connecting axis C
By adjusting the angle Θjc between the rotating body Jc and the door surface, the rotating body Jc
By inserting the push spring U between the door and the door surface, the door can be stopped at the “position where the latch abuts against the door frame” and waited.
1 and 8, when the rotating body Jc is urged by the push spring U in the opposite direction to the arrow C in the figure, and the contact G2 prevents the rotation in the direction opposite to the arrow C in the figure, the push spring U is shown in FIG. Even if there is no “force acting on the door” just before closing, “(A) rotating means”
(I) Rotating means ”.

Since one of the links of the four-bar rotation mechanism is a link device that replaces the spring, the rotation of the link A and the rotation of the door D operate independently, and the door D stops when the latch comes into contact with the link A. When rotating, the rotating body Jc rotates in the direction of arrow C in the figure,
When the door D rotates at a high speed when the latch contacts, and the rotation of the link A is delayed with respect to the rotation of the door D,
The wheel BB is locked to the door frame W via the sliding surface K3, and the rotating body Jc rotates in the opposite direction to the arrow C in the drawing and engages with the contact G2 so as to be relatively integrated with the door D so that the door is closed. Stop. Fig. 9
The sliding surface Kd attached to the door D shown in (c) is a means for restraining the rotation of the link A by engaging with the wheel B in the middle of the rotation of the link A, and the wheel B is moved on the sliding surface K1. When moving on the sliding surface K3 at the same time, the revolution of the connecting shaft C around the pivot axis O substantially stops, and when the door D continues to rotate, the wheel B is engaged.
Thus, when the drive unit and the door D operate separately without being interlocked, the rotational speed of the door due to the inertial force of the door and the rotational speed of the door due to the rotation of the link A are different. Doing exercise that is out of motion. The speed reducing means of the sliding surface Kd is such that when the door inertia force deviates from the predetermined motion, the braking means works. When the door inertia force disappears, the link device returns to the predetermined motion and the braking means does not work. Become.

FIGS. 9D to 9G illustrate the role of the spring when the spring is attached to the sealing device of FIGS. 9D to 9G. When the spring expanded and contracted by the door inertia force is restored. Explain that there is an action to open the door, but the door does not open by the sealing force acting at the same time as the spring expands and contracts due to the inertial force of the door.
The sealing device shown in FIGS. 9D to 9G is such that the sealing prevention wheel BB has a sealing function, and the wheel B can be omitted. The sealing surface K3 for sealing prevention and the sliding surface K1 for sealing are provided on the “sliding surface K rotatably supported around the support shaft Sk provided on the door frame W”. Push springs U1 and U2 are attached to both sides of the. The sliding surface K2 is omitted. The pressing spring U3 biases the rotating body Jc in the direction of arrow C in the figure. The rotation of the rotating body Jc in the direction of the arrow C in the drawing is prevented by the contact between the side surface of the rotating body Jc and the door surface. When the rotation axis Cj of the rotating body Jc is provided at a position close to the pivot axis O, the restoring force of the push spring U3 acts in the direction of opening the door, so the rotation axis Cj of the rotating body Jc is provided at a position away from the pivot axis O.
FIG. 9 (d) shows a state in which the rotation axis C of the link A crosses the axial axis Zv of the spring, and the link A is separated from G1 and is about to rotate in the direction indicated by the arrow A in FIG. Indicates. In addition, the door inertia force is large, and the state where the wheel BB is in contact with the sliding surface K3 without hitting the link A and coming off from G1 is shown. Since the angle Θak is an acute angle, the rotation of the link A is prevented and the rotation of the door D in the direction indicated by the arrow B continues, the sliding surface K rotates in the direction indicated by the arrow D, and the push spring U2 is contracted. . The door inertia force is absorbed by the push spring U2, and the door is decelerated.

FIG. 9 (e) shows a state in which the compressed spring U2 is extended. The sliding surface K rotates about the support shaft Sk in the direction opposite to the arrow D in the figure, the rotating body Jc rotates about the rotation axis Cj in the direction opposite to the arrow C in the figure, and the push spring U3 does not contract. At the same time, the angle Θak changes from an acute angle to an obtuse angle, and the link A is connected to the connecting axis C
It becomes possible to rotate in the direction of arrow A in the figure around the axis.
FIG. 9 (f) shows that the wheel BB moves from the sliding surface K3 to the sliding surface K1 and presses the sliding surface K1 due to the rotation of the link A in the direction of arrow A in FIG. In the figure, the push spring U1 is rotated in the direction opposite to the arrow D and the compressed state is shown. The push spring U2 is separated from the door frame W and becomes invalid. Further, the rotating body Jc is rotated in the direction of arrow C in the figure.
FIG. 9G shows that the link A further rotates while the door is stopped at the time of latch contact, the side surface of the rotating body Jc contacts the door surface, and the rotating body Jc and the door D are relatively integrated. Thus, the sliding surface K is further rotated to further contract the pressing spring U1, and a state in which “the force for indenting the latch” is stored in the pressing spring U1 is shown.

When the force is stored in the spring, it takes time when the load is applied, but when the spring is loosened, it takes time when the load disappears.
9D to 9G, the link A and the rotating body Jc rotate alternately while the door is slightly rotated, and the sealing device performs a plurality of operations, and these operations are the rotation of the door. Regardless of whether or not the operation is performed in an instant rather than in an instant, it takes a long time to slightly rotate the door, and the door is decelerated to a state close to stopping.
Multiple operations of these sealing devices are possible even if the push springs U1, U2, U3 are very weak springs or if the push springs are not attached.

FIG. 10 is a plan view for explaining the rotation mechanism and the impact noise elimination effect of the “opening / closing device in which the connecting shaft C is movably attached to the door”. The rotating device in FIG. 10 is the rotating body Jc in FIGS. When the door D is the first door and the door D is the second door, the driving force transmitted to the first door in the “(A) range” is insulated in the “switching range” and in the “(A) range”. "The biasing force prepared for the second door"
Seals the door and relays from rotating to sealing. The structure is the same as that of FIG. 9 except that the spring of the rotating device and the spring of the sealing device are separated, and not the acting force distance Lo but the strength of the spring, “(A) range” and “(A) range”. Thus, forces of different magnitudes act on the door, and the device is downsized by reducing the acting force distance Lo by strengthening the spring of the sealing device.
In addition, by attaching the first door between the drive unit and the door, the door keeps rotating with “(a) rotating means” while the latch is in contact with the door frame, and the “switching means” is the latch door. It can be operated after contacting the frame.

First, the rotation mechanism will be described with reference to FIGS. The door shown in FIGS. 10E and 10F is a door including a first door A, a second door D, and biasing means V and U, and a tension spring V as a biasing means of the first door A. As a biasing means for the second door D. FIG.
The solid line in (e) shows a state where the latch male part Rd comes into contact with the sliding surface part Rww of the female part Rw and the door is stationary. The pull spring V has a force to rotate the door, but no “force to dent the latch”. The force of the tension spring V is increased and the link A is rotated about the connection axis C in the direction of the arrow A in the drawing to push the spring U
When the pressure is contracted, “the force to dent the latch” is stored in the push spring U. “The force of the pulling spring V in a state where the pressing spring U is extended” shown by the solid line in FIG. 10E is “a force that only rotates the door”, which is very weak. The “force of the tension spring V when the push spring U is contracted” shown by the broken line in FIG. The force of the tension spring V
When the door is closed by setting “force sufficient to rotate the door”, it stops in the state indicated by the solid line in FIG. When closing by setting the force of the pulling spring V to “the force to dent the latch”, FIG.
The state shown by the broken line in e) is followed by depression of the latch.

As shown in FIG. 10 (f), the contact Ga prevents the force of the pulling spring V from acting on the door by preventing the "rotation of the link A in the direction of arrow A in the figure" at the time of latch contact. After contact, the push spring U extends to rotate the door D in the direction of arrow B in the figure. The force for sealing the door is determined by the length of the push spring U when the link A is hit and locked to Ga as shown in FIG. The door is pressed against the door with a force corresponding to the length of the push spring U when it abuts.
If the rigidity of the push spring U is set to be small, the link A is locked to the contact Ga because the spring does not expand or contract greatly to reach the “force to seal the door” or “force to press the door against the door”. The length of the pressing spring U is greatly different from the natural length.
When the rigidity of the push spring U is set to be large, the link A approaches the state of being fixed to the door D, and when the rigidity of the push spring U is set to be small, the push spring U is greatly expanded and contracted to gradually increase the rotational force. Not to provide to.

In order to seal the door, the force of the pulling spring V is the “force to dent the latch” when the latch contacts, and the “force to dent the latch” is stored in the push spring U as shown in FIG. You have to be ready. In this case, the spring force is excessive in the “range (A)”, the door inertia force becomes large, and the door is sealed without being decelerated at the time of latch contact. For this reason, the “force acting on the door” needs to be switched from small to large while the door stops or slightly rotates just before closing. In the above embodiment, the door is switched from small to large with no or little rotation of the door at the predetermined opening degree of the door at the time of latch contact.

When the stiffness of the spring is set to infinity, the mounting shaft is fixed, the door and the telescopic part work together, and when the stiffness of the spring is set to zero, the mounting shaft is not fixed and can move freely so,
The door and the telescopic part do not interlock, and the telescopic part continues to rotate independently without rotating the door. When the rigidity of the spring is set to be small, the expansion / contraction part provides a rotational force little by little to the door while greatly expanding and contracting the spring. The expansion / contraction part provides the door, but even if it is large, it can be limited by setting the upper limit of the expansion / contraction of the spring.

The state at the time of the latch contact shown in FIG. 10 (f) includes the case where the push spring U latch is extended and the latch contact is reached, and the case where the push spring U is contracted and the latch contact is reached. Figure 2
As described later in FIG. 2, when the air resistance applied to the door surface before the latch and contact is large and the air resistance disappears at the time of the latch contact, or when the door is difficult to move with static inertia, the push spring U This is the case when the latch comes into contact with shrinkage. When excessive force is applied from the state where the force is balanced and moves at a constant speed, it accelerates, but when it is difficult to move with static inertia attached, it does not accelerate so much that it becomes a problem even if excessive force is applied, Even if "the force to dent the latch" is excessively applied to the spring in the range of (A), when the door is moved around, the push spring U does not start to contract when the latch contacts like the former. In addition, the force acting on the door does not increase gradually, but the maximum force of “the force to dent the latch” is stored in the push spring U in advance.
When the latch comes into contact, the maximum force is applied from the beginning, and when the latch is recessed, the “force acting on the door” decreases and the door is sealed.

FIGS. 10A to 10D show an embodiment in which the latter push spring U is contracted and reaches the time of latch contact, and the force acting on the door gradually increases as in the former case. is there. FIG.
10 (a), the rotation device of (a) to (d) merely pulls the “mounting shaft Sa attached to the door via the link A” as shown in FIG. As shown in (a), in “range (A)”, “rotating body J pivotally supported around a support shaft Cj provided on door D and mounted with wheel B at the tip” is toggle spring VV. The wheel B is urged in the opposite direction to the arrow A in the figure and Gj prevents rotation in the same direction, and the wheel B comes into contact with the sliding surface K1 at the time of latch contact as shown in FIG. When the rotating body J rotates in the direction indicated by the arrow A in the figure by the inertial force and the toggle spring VV crosses the support shaft Cj, the wheel B is linked to the link A as shown in FIG.
, The link A rotates in the direction opposite to the arrow B in the figure, so that the tension spring V is stretched, and the acting force distance Lo is increased so that the tension spring V The force is changed from “a force that rotates the door” to “a force that causes the latch to be recessed”.

Although the latch is recessed at the same time as the force of the pulling spring V reaches the “force for indenting the latch”, the closing device and the door D remain relatively integrated as shown in FIG. Rotate to. Although the process of rotating and sealing in the state shown in FIG. 10C is not shown, an operation in which the tension spring V contracts is recognized. By contracting the tension spring V, the “force acting on the door” is not increased but decreased in the process until the latch is recessed and the latch male part Rd fits into the female part Rw. It is most important to reduce the impact noise at the time of closing, that no impact load is applied to “the end of the closing rotation in which the latch male part Rd fits into the female part Rw”. The speed reducing means prevents the door inertia force from disappearing at the end of the closing rotation so that an impact load is not applied.
10 (a) to 10 (d), the operating point Sa of "the force that rotates the door" is closer to the pivot O than the operating point b of "the force that causes the latch to be depressed", and the sealing device is the rotating device. It is closer to the pivot axis O. Thus, by consolidating the functions of the opening / closing device in the vicinity of the pivot O, the device is downsized.

When the wheel B comes into contact with the sliding surface K1, the force with which the link A presses the wheel B increases as the door inertia force increases, and the rotation of the rotating body J is delayed. The rotation of link A in the direction of arrow B in the figure stops,
The “force acting on the door” becomes zero, and the door is decelerated rapidly.
Even when the force of the toggle spring VV is strong, the force that acts at the time of sealing is “the force when the tension spring V is stretched”, and when the door is opened by setting the “force to dent the latch” to the minimum necessary The door never feels heavy.
As shown in FIG. 10C, the door can be sealed by the wheel B pressing the sliding surface K3. However, before the wheel B presses the sliding surface K3, the “arrow in the drawing of the rotating body J” is displayed. The rotation in the direction “b” is prevented by Gj. In the process of opening the door as shown in FIG. 10 (c) when the wheel Bb sharing the wheel rotation axis Ib is mounted on the opposite side of the surface to which the wheel B of the rotating body J is attached, the wheel Bb follows the sliding surface K3. When the rotary body J rotates in the direction opposite to the arrow A in the figure and the toggle spring VV crosses the support shaft Cj again, the sealing device returns to the state shown in FIG. The range until the toggle spring VV again crosses the support shaft Cj is the “(i) range” in the closing process, and even if the hand is released in this range, the door is sealed. Even if the toggle spring VV is released again after crossing the support shaft Cj, the door inertia force grows by the time of latch contact, and the rotating body J is rotated in the direction of arrow A in the figure.

FIG. 11 is a link device in which “link A with a bending force as in FIG. 1” is connected by a sliding pair.
It is an operation explanatory plan view of an opening / closing device provided with a releasable restraining means for transferring the action point of “force acting on the door” from the vicinity of the pivot axis O to the far side. FIG. 11A shows a solid line when fully closed, and a broken line showing the operation immediately after the fully opened state. FIG. 11 includes “switching means” that does not employ the tension spring V as a component of the link device as in FIGS. 8 and 9 and continues to operate even when the door is stopped.
The rotating body J rotates about the fixed support shaft Sw in the direction of arrow A in the figure, and the wheel B is mounted at a position far from the fixed support shaft Sw and a wheel BB is mounted at a position substantially perpendicular to the fixed support shaft Sw. It moves along a “sliding surface K provided on the door D at a position close to the pivot O” and a “sliding surface KK provided on the door D at a position far from the pivot O”. In “range (a)”, the wheel B presses the sliding surface K, and the wheel BB separates from the sliding surface KK. In the “range (ii)”, the wheel BB presses the sliding surface KK, and the wheel B is separated from the sliding surface K.
In FIG. 11A, as in FIG. 1, the wheel B presses the sliding surface K while the angle Θak is an acute angle, and the door D rotates about the pivot O in the direction indicated by the arrow B in the figure. To do. In the “range (a)”, the action point is stopped at a position close to the pivot axis O, and the action force distance Lo is made small and the drive force distance Lv is kept large. The wheel B separates from the sliding surface K when the angle Θak is a right angle in the “switching range”, and the “restraint means for stopping the action point at a position close to the pivot axis O” is released. In the “range (ii)”, the wheel BB presses the sliding surface KK while moving along the sliding surface KK. The acting force distance Lo is large and the driving force distance Lv is small.

The door D and the door frame W rotate relative to each other while sharing the rotation axis O. FIG. 11A is an explanatory view of the operation of the door D rotating around the pivot O in a state where the door frame W is fixed. FIGS. 11B and 11C are views of the pivot O in a state where the door D is fixed. It is operation explanatory drawing that the door frame W rotates around, and the fixed support shaft Sw
Revolves around the axis O.
As shown in FIG. 11B, the fixed support shaft Sw is rotatably attached to the door frame W on a “rotary body Jsw that rotates about the fixed support shaft Sw provided on the door frame W”. FIG. 11B is an operation explanatory diagram in the case where the position of the fixed support shaft Sw is not retracted from the door, and FIG. 11C is an operation explanatory view in the case where the fixed support shaft Sw is retracted from the door. "(A) range" where the force to rotate the door is weak
Then, the rotating body Jsw is rotated in the direction indicated by the arrow C by the push spring U, and the fixed support shaft Sw is retracted from the door as shown in FIG. 11C. It becomes difficult to move on the sliding surface KK due to frictional resistance. As it is sealed, the push spring U contracts, the fixed support shaft Sw approaches the door, and the wheel BB easily moves on the sliding surface KK.

If the door inertia force is large immediately before the fully closed state, the wheel BB reaches the end portion KKE of the sliding surface K after the door is closed. When the door inertia force is large, the wheel BB reaches the end portion KKe of the sliding surface K and the door is closed. The sliding surface Kbb shown in FIG. 11B is “supported rotatably around the support shaft Sd on which the door D is provided, and is urged by the pressing spring Ubb to face the sliding surface KK. And the sliding surface KK form a passage through which the wheel BB barely passes.The sliding surface Kbb engages with the door immediately before fully closed, and the push spring Ubb contracts to absorb the door inertia force. However, when the inertial force is large, the impact sound can be sufficiently reduced only by preventing the wheel BB from reaching the terminal end KKe of the sliding surface K after the door is closed.
When the push spring Ubb is restored, the door urges in the direction of opening, but the wheel BB immediately slides on the sliding surface KK.
The door closes soon after opening. “The force by which the sliding surface KK presses the wheel BB” is a force toward the center of revolution of the wheel BB and does not greatly resist the movement of the wheel BB even if it is large. Thus, the means for decelerating the door does not decelerate the door, but decelerates the movement of the wheel BB, and works effectively over a wide range of the magnitude of the door inertia force.

FIGS. 12 to 16 are operation explanation plan views of the opening / closing device inherited from the “rotating device having a position close to the pivot O as an action point” to the “sealing device having a position far from the axis O as an action point”. The switchgear is a device that reduces the size of the device despite the large area in which the device operates. FIG.
The switchgear of -15 adds a sealing device to the switchgear of FIGS. 1-3, and the switchgear of FIG. 16 adds a sealing device to the switchgear of FIG.
The rotating means and switching means of the switchgear shown in FIG. 12 are provided with a sliding surface K1 near the pivot axis O and a “link A1 with a wheel B1 attached to the tip portion”. It moves while pressing the sliding surface, and a bending force acts on the link A. The sealing means is provided with a "link A2 with a wheel B2 attached to the tip" and a sliding surface K2 that moves along the axis O in the vicinity of the pivot O, and the wheel presses the sliding surface in the same manner as in FIGS. Therefore, the link A1 and the link A2 are connected by the link A3.
The link A2 is urged by a pulling spring V, and one end of the pulling spring V is attached to the support shaft Sa at the tip of the link AA and the other is attached to the support shaft Sww provided with the door frame W. The link AA swings between G1 and G2 and is pivotally supported by the link A2.

The “switching means provided in the vicinity of the pivot axis O” of the switchgear of FIG. 12 is “(A)” as in the switchgear of FIG.
The "switching means" that keeps the acting force distance Lo small in the range of "and is largely switched at the time of sealing" is sufficient as an opening / closing device. When this is increased to increase the acting force distance Lo, the opening / closing device of FIG. 1 is obtained, or when the spring force is increased, the opening / closing device of FIG. 1 is reduced.
The switchgear in FIG. 12 is made smaller than the switchgear in FIG. 1 so that only “(A) rotating means” and “switching means” are provided, and “(I) rotating means” is handled by the sealing device. The apparatus is miniaturized by largely transferring the action point, and the action point is pivoted as shown in FIGS.
The operating range of the device becomes smaller compared to the one that gradually moves away from the one or the one that “rotary body provided with the rotary shaft at a position far from the pivot axis O” as shown in FIGS. Sometimes it can be housed in an elongated case along the door frame W.
In addition, the large movement of the “switching means” causes the sealing device at a position far away from the pivot axis O to move greatly, and within the slight rotation range of the door of “(range)”, “sealing while decelerating” The operation with a long passage of time such as “the operation to reach the door” or “the operation to reach the seal while the force acting on the door is gradually performed” is performed.

The base end portion Ko1 of the sliding surface K1 shown in FIG.
), The wheel B is kept in the vicinity of the pivot axis O within the range “(A)”. As shown in FIG. 12 (b), the locking means is released at a predetermined opening, and the wheel B instantaneously leaves the pivot O. Link A
The rotation is small while it is locked in the recess and is large after it is detached from the recess.
The cause of the impact sound at the time of closing is further acceleration of the “(range)”, and it is desirable that the range of rotation with as strong a force as possible is small. As described in FIG. 10, the drive unit and the door are first.
When the door is attached indirectly via the door, the latch can come into contact with the door frame and wait before the “switching means” operates, but when the drive unit and the door are directly attached, the “switching means” The latch does not always stand by abutting against the door frame before the operation. Further, the opening degree of the door when the “switching means” starts can be within a certain range when the angle Θak is a right angle, but cannot be determined to a limited value. In this case, the opening degree of the door when the wheel B which is relatively locked is separated is determined to some extent. Also, it must be ensured that the locked wheel B does not stop when it comes off. In any case, it is desirable that the door rotation range from the latch contact time to the fully closed state is small and the opening degree of the door on which the “switching means” operates is determined as small as possible.
The “means for disengaging the dent and the wheel B” shown in FIG. 12 is such that the opening degree of the door when the “switching means” is started is made as small as possible so as to be close to the time of latch contact.

The “sealing device provided near the axis O” is a sliding surface K2 that engages and disengages from the wheel B2 as shown in FIGS.
The sliding surface K2 is rotatably supported around a connection axis C provided on the door. The pressing spring U attached to the “surface facing the door frame W of the base end portion Ko2 of the sliding surface K2” engages with the door frame W in “range (A)” and disengages in “range (I)”. . Switching range as shown in FIG.
In the “range (ii)”, the wheel B2 and the sliding surface K2 are engaged, and the push spring U is engaged with the door frame W. Since the pressing spring U is supported by the door frame W and the wheel B2 is supported by the door frame W via the link A2, the sliding surface K2 is sandwiched between the pressing spring U and the wheel B2 and cannot move. Sliding surface K
2 is fixed to the door frame W, and the door is also fixed to the door frame W via the sliding surface K2 and is stationary.
The pressing spring U is provided near the base end Ko2 of the sliding surface K2, and when the wheel B2 presses the sliding surface K2 farther from the pivot O than the pressing spring U, “the wheel B2 presses the sliding surface K2. The force Fb "acts in the direction in which the connecting shaft C rotates in the direction of the arrow C in the figure with the pressing spring U as a fulcrum, and the sliding surface K2 acts as a lever that springs up the connecting shaft C with the pressing spring U as a fulcrum. Although the door is returned to the opening direction by the restoring force of the contracted spring, as shown in FIG. 12C, when the wheel B2 reaches the terminal portion Ke2 of the sliding surface K2 and the contact Gk contacts the door surface. When the door D and the sliding surface K2 are relatively integrated with each other, the wheel B2 prevents the "rotation returning also in the door opening direction".

Until the wheel B2 reaches the end portion Ke2 of the sliding surface K2, the push spring U contracts but does not extend. The retracted spring will not be restored without restoring the door. Wheel B2 is sliding surface K2
When moving up and away from the pivot axis O, the door rotates in proportion to the amount by which the push spring U contracts, resulting in sealing. The force of the pulling spring V is reduced in proportion to the amount by which the pressing spring U contracts.
However, the force stored in the pusher spring U works in the direction to open the door and lightens the door. Even if the force to rotate the door is simply reduced, the door is not made heavy when the door is opened.
When the door is closed and rotated while the push spring U is contracted, the push spring U resists the door inertia force and functions as a deceleration means. Receiving the inertial force with a spring causes the reaction force of the door inertial force to work in the direction of opening the door, but in this way the door inertial force is absorbed into the spring while allowing the door to move,
If the spring is restored and the door is not pushed back, the door inertia force is converted into the braking force.
The “decelerator that operates immediately before sealing” in FIGS. 12 to 14 is also a sealing preventing means, and the driving force by the “spring that works in the direction of closing the door” and the resistance by the “spring that works in the direction of opening the door” When the door is closed, the door is closed between the door closing force and the door stop Gd. It is something to sandwich. 12 to 14, the rotating device plays a role of preventing the door from rotating in the opening direction by rotating the door in the “(range)”.

The force of the tension spring V is set so that the movement of the wheel B2 stops on the way to the end portion Ke2 even when there is no door inertia force. As the door inertia force increases, the door D rotates more in the direction indicated by the arrow B in the figure, the sliding surface K2 rotates about the connection axis C in the direction opposite to the arrow C in the figure, the angle Θak increases, and the push spring U Since the amount of shrinkage increases, a large resistance is given to the movement of the wheel B2. As described above, even if the door inertia force disappears, the door does not return in the opening direction, and thus the large resistance does not decrease.
As the wheel B2 moves on the sliding surface K2 farther from the pivot axis O than the pressing spring U, the pressing spring U does not affect the movement of the wheel B2, but "the force Fb that the wheel B2 presses the sliding surface K2" Even if is large, “the force acting in the direction in which the wheel B moves on the sliding surface K2” is small. This means that the movement of the wheel B does not stop no matter how large the inertia force of the push spring U is. means. The sealing device shown in FIG. 12 stops the door no matter how large the door inertia force is. Rather than blocking the seal, the door is temporarily stopped before it is sealed.
The amount by which the push spring U contracts when fully closed is the maximum and is constant regardless of the magnitude of the door inertia force. Regardless of whether the door stops in the middle or not, the link AA rotates in the direction indicated by the arrow D in the figure and reaches the acting force distance Lo2 in the middle of reaching the end portion Ke2. Thus, the force of the tension spring V is set so as to overcome the maximum force of the push spring U and reach the wheel B2 to the end portion Ke2 of the sliding surface K2.
When the contact Gk comes into contact with the door surface as shown in FIG. 12C, the sliding surface K2 and the door D are relatively integrated, and the door is sealed. The sealing device shown in FIG. 12 is moved parallel to the vicinity of the pivot axis O, and the recess of the base end portion Ko1 of the sliding surface K1 is attached to the base end portion of the sliding surface K2. If it matches, it will be fully established as a switching device. The switchgear is also a “sealing device” with “(a) rotating means” added.
As described above, various kinds of switchgears including the rotation device, the switching device, and the sealing device are taken out by taking out any of the rotation device, the switching device, and the sealing device from each of the switching devices shown in the plurality of embodiments. It is natural to be done.

The sealing device shown in FIG. 12 increases the “force acting on the door” by shifting the point of action far, and further increases the time between the contact of the latch and the fully closed state. By adding a slight force, the "force to dent the latch" is finely adjusted so that the door closes quietly. If the door is fully closed in an instant after the latch contact, the operation of closing the door again will not be permitted. While the door is rotating slightly, the “force acting on the door” is insufficient to the “force that dents the latch” and the door stops, and the “force acting on the door” further gradually with the door stopped. In order for the operation to grow and dent the latch to be executed over time, the door must be stopped immediately before the fully closed state. In the case of FIG. 12, the door is stopped regardless of the opening degree of the closing, whether it is closed from the fully opened position or from the slightly opened position, and this resistance is overcome and the door is sealed.

If the door is rotated with a sealing device far from the pivot O at the end of closing, when the door is opened, the sealing device is started first, and the “switching means” close to the pivot O follows with a delay.
If the shape from the depression of the sliding surface K1 to the terminal end Ke1 is a curve having a larger curvature than the “circular orbit Rb1 at the point farthest from the fixed support shaft Sw1 of the wheel B1,” the movement direction of the wheel B when the door is opened The angle Θak becomes an acute angle to reversely rotate the link device. In this case, the door and the drive unit are interlocked in the entire rotation range, and it is not a “switching means” that does not involve any rotation of the door, but almost no “
“Switching means”, and the drive unit interlocks with the door in the “switching range” and “(i) range”, so that the “spring that is expanded and contracted by the door inertia force” is restored and the door is rotated in the opening direction. It prevents that.
For example, when the end portion Ke2 of the sliding surface K2 is arranged on the side close to the pivot axis O and the connecting shaft C is arranged on the far side, the movement of the sliding surface K2 pushing up the connecting shaft C is not blocked by the pivot axis O. The door rotates in the opening direction. In this case, when the drive unit is interlocked with the door, the force to open the door is also blocked by the link A1 of the “switching means provided in the vicinity of the pivot axis O”, and the door is not returned in the opening direction.

12 (d) to 12 (f) show the rotating device of FIGS. 12 (a) to 12 (c) separately from the urging means of the sealing device. A2 is biased by a toggle spring VV so that different forces are applied to the door in the “(A) range” and “(A) range”. By strengthening the toggle spring VV, the sealing device can be brought closer to the pivot O and the device can be miniaturized.
The connecting portion between the link A2 and the link A3 is attached so that the rotation axis Ib2 of the wheel at the end of the link A2 can reciprocate along the long hole H provided in the link A3. The torsion spring UV is relayed to the toggle spring VV. Wheel B1 in "(A) range"
Presses the sliding surface K1 to rotate the door. As shown in FIG. 12D, when the rotation of the link A1 hits and is locked by GA1, the wheel B1 leaves the sliding surface K1. The rotation of the link A1 is not transmitted to the door. At the same time, the rotational axis Ib2 of the wheel is pushed out by the proximal end Ho of the long hole H, and as shown by the broken line in FIG. Rotate in the direction of arrow a. Toggle spring VV is link A
Crossing the second rotation axis Sw, the link A2 continues to rotate until it comes into contact with the GA21.

When the link A2 is in contact with the contact GA21 and is in a standby state, the wheel B2 is not in contact with the sliding surface K2, and when the link A1 is in contact with the contact GA21, the sliding surface K2 is in contact with the wheel B2. The position is in contact. Before the link A1 hits the GA21, the standby state is canceled and the wheel B is located closer to the door frame W than the sliding surface K2 to prevent the door from closing. It is in a position far from “the center of rotation Sw2 of A2”.
As shown by the broken line in FIG. 12D, the “(A) rotating means” is in a standby state with a large force so that the axis of the toggle spring VV moves greatly and crosses the “rotation center Sw2 of the link A2”. In the "(A) range", the wheel B1 presses a position near the pivot axis O of the sliding surface K1, so that a large force acts on the door smallly.

Initially, when the toggle spring VV crosses the rotation axis Sw of the link A2, the expansion and contraction of the toggle spring VV is small, and the link A2 is insulated from the door, but starts to rotate very slowly. During this time, the door continues to rotate with dynamic inertia.
The rotational speed of the link A2 is constant, and the rotational speed of the door varies depending on the closing start opening.
When the closing start opening is large, the door rotates greatly until the link A2 rotates and the wheel B2 presses the sliding surface K2, so that the wheel B slides on the sliding surface K3 as shown in FIG. Will be pressed.
The sliding surface K3 is rotatably supported around the "supporting shaft Ik3 provided on the door", and is urged by the torsion spring UV3 in the direction indicated by the arrow D in FIG. The sliding surface K3 rotates greatly in the opposite direction to the arrow D in the figure until the link A2 rotates and the wheel B2 presses the sliding surface K2, and the angle Θak increases to increase the angle of the wheel B. Large resistance to movement in the direction of the middle arrow e. That is, the greater the rotational speed immediately before closing the door, the greater the braking force.
FIG. 12 (f) shows a state in which the wheel B3 is separated from the sliding surface K3 when sealed, and the wheel B2 “presses the sliding surface K2 in contact with the door D”.

“The magnitude of the inertial force of the door just before closing and the rotational speed of the door” differ greatly depending on the opening degree of the closing. If the form of the link device changes according to the magnitude of the door inertia force just before closing,
The magnitude of the braking force can be changed by changing the form. Further, if the magnitude of the door inertia force can be measured by changing the length of the spring, the magnitude of the braking force can be changed by the length of the spring.
12 (d) to 12 (f), “(i) Rotating means” stands by in “(A) range” and “Switching range” is started by “(A) Rotating means”. In the “range”, set a certain period of time during which the “force acting on the door” does not work. Measure the “intensity of the door inertia force and the rotation speed of the door just before closing” at the door movement distance within a certain time The braking force according to “the magnitude of the inertial force of the door just before closing and the rotational speed of the door” is applied to the moving distance of the door within a certain time.

When the impact noise is reduced only by the speed reduction means taken immediately before the fully closed state as in the sliding surface Kbb shown in FIG. 11B, the door speed immediately before closing is within a certain range. Only when the door is adjusted to a specific state. In order for the door closer to adapt to various doors, the spring must be strengthened. The door must be closed with a strong spring and sealed even if the speed of the door immediately before closing becomes high. Even if it is sealed with a strong spring, it must be prevented from accelerating in the “(I) range” and not having a large force when fully closed. Also, it must correspond to the “door inertia force immediately before closing” which varies depending on the opening degree of opening.
The speed reducer of the opening and closing device shown in FIGS. 13 and 14 changes the magnitude of the braking force in accordance with the magnitude of the door inertia force. The magnitude of “force” falls within a certain range.
The rotating means and switching means of the opening / closing device shown in FIG. 13 are provided with the opening / closing device of FIG. 7 in the vicinity of the pivot O. Rotating body J that is rotatably supported ”and“ Link A1 with wheel B1 attached to the tip ”are connected by connecting shaft P, and wheel B1 presses sliding surface K1 in the same manner as in FIGS. The link A1 has a compressive force.
The sealing means is provided in the vicinity of the pivot O, and the “link A2 with the wheel B2 attached to the tip” is rotatably supported around the fixed support shaft Sw2, and the link A3 connects the link A1 and the link A2. The link A2 is rotated in the direction of arrow C in the figure. The sliding surface K2 moving along the wheel B2 is a rotating body J
Attach to door D via c.

The rotating means and switching means in the vicinity of the pivot axis O will be described.
A broken line shown in FIG. 13A is an operation explanation plan view of “range (A)”, and a solid line shows a state just before closing. The sliding surface K1 that moves along the wheel B1 is rotatably supported around the connection axis C,
The rotation in the direction of the arrow in the figure is prevented by the hit Gc. A recess provided in the base end portion K1o of the sliding surface K1 keeps the acting force distance Lo small by locking the wheel B1 in the “range (A)”. As shown by C90 in the figure, the sliding surface K1 remains in contact with the contact Gc from the fully open state to the middle of closing, and as shown by C30 in the figure, the sliding surface K1 starts from the contact Gc. The “side surface of the sliding surface K opposite to the side on which the wheel B1 moves” moves along the wheel BK provided on the door frame W. Depending on the position of the wheel BK, the opening degree of the door from which the wheel B1 is detached from the recess can be freely designed. As shown in FIG. 13C, when the door is opened by making the sliding surface K1 rotatable, the “wheel B1 staying at the terminal end K1e of the sliding surface K1” returns to the base end K1o. The door opening can be reduced.
The “switching means” of the present invention changes the “force acting on the door” abruptly to move the action point or action line far from the pivot axis O. In the process of opening the door as the instantaneous movement distance increases. When the “(i) rotating means” returns to “(a) rotating means”, the opening of the door increases. It is desirable that the range of rotation with as strong a force as possible is small. The releasable restraining means described in FIGS. 13 and 14 increases the instantaneous moving distance as much as possible and returns as soon as possible when the door is opened.

The sealing means and the speed reduction means near the axis O will be described.
The rotating body Jc is urged by an urging means (not shown) around the connecting shaft Cj in the direction of the arrow D in the drawing and is pivotally supported so that Gj is prevented from rotating in the same direction. The sliding surface K2 is weakly biased by a biasing means (not shown) in the direction of arrow E in the figure around a connecting shaft Ck provided at the tip of the rotating body Jc and is rotatably supported. G1 prevents rotation in the same direction. One side moving away from the door frame W with the connecting axis Ck of the sliding surface K2 in the middle is the sliding surface K2 on which the wheel B2 moves, and the wheel B3 is attached to the other tip end approaching the door frame W.
The state diagram at the time of latch contact shown in FIGS. 13 (a) and 13 (b) is a state diagram in which the wheel B1 is detached from the concave portion of the sliding surface K1 and moves toward the terminal portion Ke1 in the direction indicated by the arrow G in FIG. And link A2
FIG. 6 is a state diagram in which the wheel B2 presses the sliding surface K2 to overcome the weak urging force in the direction indicated by the arrow E and rotate in the direction opposite to the direction E in the figure.

FIG. 13A shows a state in which the door inertia force is small, and the door is stationary when the latch is in contact. The wheel B3 does not contact the sliding surface K3 provided on the door frame W, but around the connecting shaft Ck. As shown in FIG. 13C, the wheel B2 reaches the terminal portion Ke2 of the sliding surface K2. At this time, the rotation of the sliding surface K2 in the direction opposite to the direction of h is prevented by the contact G2, the rotation of the rotating body Jc in the direction of the arrow D is blocked by the contact Gj, and the sliding surface K2 and the rotating body Jc are separated from the door D. And the door is sealed by the force Fb2 that the wheel B2 presses the sliding surface K2.
FIG. 13B shows a state in which the door inertia force is large and the door continues to rotate at the time of latch contact. The wheel B3 comes into contact with the sliding surface K3, and the rotating body Jc passes around the connection shaft Cj. And rotate in the opposite direction
The angle Θak shifts from a right angle to an acute angle. As the door inertia force increases, the door continues to rotate, the rotating body Jc rotates more, the angle Θak becomes more acute, and the wheel B3 becomes difficult to move on the sliding surface K3 in the direction indicated by the arrow in the figure. Further, as the angle Θak becomes sharper, as the wheel B3 moves on the sliding surface K3, the rotating body Jc rotates more in the opposite direction, and the point of action of the force that the wheel B2 presses the sliding surface K2 becomes larger. It approaches the rotation axis Ck of the sliding surface K2. As a result, the greater the inertial force of the door, the greater the resistance to rotation of the sliding surface K2 in the direction opposite to the direction of E, and the door is decelerated.

FIG. 14 is similar to FIG. 13 in that the rotating means and the switching means in the vicinity of the pivot axis O have a structure in which the rotating body J and the link A1 are connected by a connecting shaft P.
Wear. A torsion spring UV is attached around the connecting shaft P to bias the wheel B1 away from the fixed support shaft Sw1. A compressive force is acting on the link A1. The rotating body J is rotatably supported around the fixed support shaft Sw1, but the rotation direction is not constant in the closing process. Around the connecting axis P, the “intersection angle Θaj between the axis core line Zj of the rotating body J and the axis axis line Za of the link A” continues to increase during the closing process. The biasing means of the switchgear according to the present invention biases the rotation around any of the connecting shafts of the link device, but the “intersection angle of the axis lines of adjacent links” continues to increase or decrease. Limited to location.
The wheel B1 moves along the sliding surface K1 provided on the door D, and G1 hits the end of the sliding surface K1 close to the pivot axis O and G2 hits the end far from the pivot O.

A broken line shown in FIG. 14A is a plan view for explaining the operation of “range (A)”, and a solid line shows a state just before closing. As shown by B1-90 and B1-10 in the figure, the wheel B1 hits G1 from fully open to just before closing.
The wheel B1 is restrained within the “range (A)” and the acting force distance Lo is kept small. The wheel B1 moves away from the contact G1 or the contact G2 when the intersecting angle Θtk between the sliding surface K1 and the “straight line T passing through the fixed support shaft Sw1 and the wheel rotation axis Ib” is a right angle. B1
-10 indicates that the wheel B1 hits away from G1 away from the pivot O immediately before closing the magazine, and B1-20
In the process of opening the door as shown in FIG.
One end of the link A2 is rotatably connected to the link A1, and a wheel B2 is attached to the other end. The middle part of the link A2 passes through the ball spline Jc. The ball spline Jc is “a rotating body Jc that is rotatably supported around the connection axis C and provided with a groove H that moves along the axial direction of the link A2.” It is.

The sealing means of FIG. 14 is provided with a sliding surface K2 that receives the pressing force Fb of the wheel B2 and “the reaction force of the door inertia force in the opposite direction” at the same time as in FIG. The surface K2 is rotatably supported around a support shaft Ik provided at the front end portion of the “rotary body Jk that is rotatably supported by the fixed support shaft Sw2 of the door frame”. The sliding surface K2 is connected to the fixed support shaft Sww by the pulling spring VV, and the rotating body Jk is urged around the fixed support shaft Sw2 in the direction indicated by the arrow E in FIG.
blocked by j. At the same time, the sliding surface K2 is urged around the support shaft Ck in the direction of the arrow D in the figure, and rotation in the same direction is prevented by Gk.
FIGS. 14 (a) and 14 (b) are state diagrams at the time of latch contact, in which the wheel B1 is separated from G1 on the sliding surface K1 and is moving toward the contact G2, and the link A2 is illustrated. FIG. 4 is a state diagram in which the wheel B2 moves in the direction of the middle arrow C and presses the recess Ko2 of the sliding surface K2.

FIG. 14A shows a state in which the door inertia force is small, and the door is stationary when the latch is in contact, and the terminal portion Ke2 of the sliding surface K2 does not contact the sliding surface K3 provided on the door frame W. Sliding surface K2 is spindle C
As shown in FIG. 13 (c), the wheel B2 rotates around the k in the direction opposite to the arrow D in the figure.
The door is sealed by the force Fb2 that presses. The line of action of the pressing force Fb2 and the "axis axis Zk of the sliding surface K2 passing through the support shaft Ck and the action point b" are arranged in a substantially straight line, and the reaction force of the pressing force Fb2 is based on the connecting shaft C as a fulcrum. Backed by a lever A2.
FIG. 14B shows a state in which the door inertia force is large and the door continues to rotate at the time of latch contact. The rotating body Jk is separated from Gj and is opposite to the arrow e in FIG. The terminal portion Ke2 of the sliding surface K2 contacts the sliding surface K3. The sliding surface K2 acts in two directions around the support shaft Ck, and the wheel B2 resists the force Fb2 that presses the sliding surface K2. When the door inertia force is not large, the sliding surface K2 rotates around the support shaft Ck in the opposite direction from the middle of the rotation of the rotating body Jk.
The terminal portion Ke2 of the sliding surface K2 contacts the sliding surface K3.
As the door inertia force increases, the door continues to rotate, the rotating body Jk rotates more, and the distance that the terminal portion Ke2 of the sliding surface K2 moves on the sliding surface K3 becomes longer. As a result, the greater the inertial force of the door, the greater the resistance to the rotation of the sliding surface K2 in the opposite direction, and the door is decelerated.

The opening and closing apparatus described in FIGS. 13 and 14 absorbs and stores the door inertia force in the spring, and simultaneously applies a force to close the door so that the door does not return in the opening direction when the spring storing the door inertia force returns. The door is sealed. The speed reducer described in FIGS. 13 and 14 is such that the sealing device shifts to a form in which it is more difficult to move in accordance with the magnitude of the inertia force of the door, causing a situation where the sealing force is insufficient, and the door is fully closed. The closer to the point, the greater the resistance to prevent sealing.
In FIGS. 13 and 14 (a), the form in the sealed system is broken by the inertial force in FIGS. 13 and 14 (b) and returns in FIGS. 13 and 14 (c). When the surface K2 rotates while returning the central axis Ck of the rotation toward the “position in the closed system in FIGS. 13 and 14 (a)”, compared to when the central axis Ck of the rotation rotates without moving. Thus, the movement of the wheel B2 in the direction of the arrow C in the drawing is pushed back, and the movement in the direction of the arrow C in the drawing is delayed accordingly.
In a normal speed reducer, when a large displacement is changed to a small displacement, the small displacement moves slowly and strongly. The action is delayed by the lack of force when converting to "large action to be applied". In FIGS. 13 and 14, when the form collapsed by the small movement of the wheel B <b> 2 in the direction of the arrow C in the drawing is restored, the force is insufficient due to the restoration with a large operation.
The speed reducer described in FIGS. 13 and 14 converts the door inertia force into a braking force, and greatly resists the door that accelerates by opening the door greatly, and resists the door that does not accelerate by opening small. To do. Like a "decelerator that tries to handle with a certain resistance", it does not work at all for doors that accelerate by opening the doors to a large extent, but keeps the doors stationary for doors that open small and do not accelerate is not.

The rotating means and switching means of the switchgear shown in FIG. 15 are similar to FIG.
Provided in the vicinity, the sliding surface K1 is rotatably supported around the connection axis C, and the rotation in the direction of the arrow in the figure is prevented by Gc. The link A1 is equipped with a "wheel B1 moving along the sliding surface K1" at one end and a sealing wheel B2 at the other end. Link A1
The ball spline Jc passes through the ball spline Jc. The ball spline Jc is rotatably supported around the fixed support shaft Sw, and is provided with a groove H that moves along the axial direction of the link A1. The tension spring V is urged in the direction of the arrow C in the figure so that the wheel B1 presses the sliding surface K1, and a tensile force is applied to the link A1.
As shown in FIG. 15 (a), the sliding surface K1 remains in contact with Gc from the time of full opening to the middle of closing in the “range (A)”. A recess provided in the base end portion Ko1 of the sliding surface K1 locks the wheel B1 and keeps the acting force distance Lo small. As shown in FIG. 15B, the sliding surface K starts from the middle of closing.
1 is separated from the contact Gc, and the “side surface of the sliding surface K opposite to the side on which the wheel B1 moves” moves along the sliding surface K3 provided on the door frame W. As soon as the moving surface K1 moves away from the sliding surface K3, "the wheel B1 staying at the terminal portion Ke1 of the sliding surface K1" returns to the base end portion Ko1. By making the sliding surface K1 rotatable, the opening degree of the door when the “wheel B1 staying at the terminal portion Ke1 of the sliding surface K1” returns to the base end portion Ko1 in the process of opening the door is reduced.
In FIG. 15B, the sliding surface K1 indicated by a broken line indicates the initial contact with the sliding surface K3, and the solid line indicates the subsequent. The wheel B1 moves in the direction opposite to the arrow C in the figure, the pulling spring V is pulled away, the "force acting on the door" changes from positive to negative, and the door is decelerated. When the sliding surface K1 is in contact with the sliding surface K3 and at the same time the angle Θak is designed to be an obtuse angle, it does not become negative. Thus, before the latch contact, the “force acting on the door” becomes a minimum value, and the door decelerates.

As shown in FIG. 15C, when the wheel B1 moves to the terminal end Ke1 of the sliding surface K1, the wheel B2 presses the sliding surface K2. The sliding surface K2 stands upright to the door surface.
When the door surface is a plane including the pivot axis O, the sliding surface K2 standing perpendicular to the door surface is a tangential direction of the circular motion with the pivot axis O as the axis, so that the position away from the door surface is When the wheel B2 is pressed in a direction away from the pivot axis O (in the direction of arrow C in the figure), the wheel B2 is moved away from the door surface (
The door D rotates in the closing direction. As wheel B2 moves away from the door surface, the door accelerates. Conversely, when the wheel B2 is pushed away from the door surface in the direction approaching the pivot axis O (the direction opposite to the arrow C in the figure), the wheel B2 moves in the direction approaching the door surface (the direction opposite to the arrow D in the figure). And the door rotates in the opening direction. As the wheel B2 approaches the door surface, the door decelerates.

The distance between the “contact point b between the wheel B2 and the sliding surface K2” and the door surface is the acting force distance Lo, and the magnitude of the “force acting on the door” is designed according to the height of the sliding surface K2. it can. Wheel B2 is sliding surface K
In the range in which the portion of the contact surface perpendicular to the door surface is moved and the line of action of the pressing force Fb is parallel to the door surface, it can be rotated by “(a) rotating means”. If it stops, the door rotates slowly. As shown in FIG. 15 (d), when the wheel B2 reaches each corner of the end portion Ke2 of the sliding surface K2, the action line of the pressing force Fb suddenly changes its direction and the “force for rotating the door” is “latched”. It grows to “the power to dent”. In the sealing device of FIG. 15, the moving distance of the wheel B2 is small and the amount of expansion and contraction of the spring is small, so that the force of the spring does not weaken.
When moving while pressing the sliding surface parallel to the “closed door surface D0” when the wheel is sealed, the longer the parallel part of the sliding surface is, the smaller the force in the moving direction of the wheel is. The speed of wheel movement is determined by the degree to which the pressing force is insufficient regardless of the length of the parallel part of the sliding surface. A vertical sliding surface is preferred. Further, even if the force that presses the vertical sliding surface is very strong, the moving speed of the wheel does not increase, so that it can be sealed quietly. Further, when the sliding surface K stands upright to the door surface and the corner portions are provided at the terminal end Ke, the sliding surface K can be sealed even with a weak force.
The sealing device that uses a vertical sliding surface and stops once before closing closes the impact sound even when a strong spring is used, and can be applied to any door.

FIG. 16 is a plan view for explaining the operation of the switching device relayed from the rotating device to the sealing device with the switching device described in FIG. 8 as “switching means”. The sealing device is controlled according to the magnitude of the door inertia force. Sealing prevention means for increasing power is provided.
As described with reference to FIGS. 1 to 3, when the wheel B is mounted on the support shaft Ib at the tip of the link A, FIG.
As described above, when a spring is attached to the support shaft Sa at the tip end of the link A, the link A rotates about the rotation shaft C, and the action line of the force passing through the support shaft at the tip end is the axis of the link A. This is the same in that the rotation direction of the link A is determined depending on which side of Za is located, and the rotation direction is switched with the boundary of “when the force action line Zv crosses the center of rotation C”. In the case of FIGS.
In the case of (1), the “(range)” is provided with means for restricting the rotation of one side of the link A, and the “switching range”
It is the same in that the restriction is released by.

The restraining means capable of releasing the “switching means” is provided in the vicinity of the pivot O, and the rotating body J is rotatably supported around the connection axis C and is urged by the pulling spring V in the direction of the arrow a in the figure. The rotation of the rotating body J in the opposite direction to i is prevented by the hit Gj. One of the tension springs V is attached to the “spring support shaft Sj provided on the rotating body J” and the other is attached to the fixed support shaft Sw.
In the “range (A)”, the contact Gj that is attached to the rotating body J engages with the door D, whereby the spring support shaft Sj is fixed to the door D and revolves around the pivot O. The line of action of the force acting on the door is the spring axis Zv, and the distance Lo is kept small in the “range (a)”. FIGS. 16 (a) and 16 (b) show a state in which the connecting shaft C crosses the spring axis Zv and the hit Gj leaves the door D and the rotating body J tries to rotate in the direction of arrow A in the figure. By making the direction of the action line Zv of the force acting on the door toward the pivot axis O of the door, a "means for reducing the force acting on the door" is taken, and the door is brought into a state of being close to or close to the state just before closing. Yes.

One end of the link A is connected to a connecting shaft P provided on the rotating body J, and the wheel B is mounted on the rotating shaft Ib of the wheel B provided on the other end. FIG. 16 (c) shows that the rotating body J rotates in the direction of the arrow a in FIG. Indicates the state to perform. The support shaft Sj and the connection shaft P are arranged radially from the connection shaft C. The support shaft Sj moves in a direction perpendicular to the “closed door surface D0” and the connection shaft P moves in a parallel direction, so that the wheel B moves. It moves greatly in parallel with the “closed door surface D0”. In the “range (ii)”, the point of action of the force Fb at which the wheel B presses the sliding surface K moves to a position far from the pivot axis O and increases the distance Lo.
It is pivotally supported around a connecting shaft Ck provided on the sliding surface K or the door D, and is urged by an urging means (not shown) in the opposite direction to the arrow D in the figure and is rotated in the direction opposite to the arrow D. Blocked by G2. The wheel Bb is rotatably supported around a fixed support shaft Sww provided on the door frame W and is urged by a push spring U in the direction of arrow E in the figure. .

FIG. 16A shows a state in which the door inertia force is small, and the door is stationary when the latch is in contact. The wheel B presses the sliding surface K and the sliding surface K is connected without contacting the wheel Bb. It rotates around the axis Ck in the direction of arrow D in the figure. As shown in FIG. 13 (c), the rotation of the sliding surface K in the direction indicated by the arrow D is blocked by the contact G1, and the sliding surface K and the door D are relatively integrated with each other, so that the wheel B becomes the sliding surface K.
The door is hermetically sealed by the force Fb that presses.
FIG. 16B shows a case where the door inertia force is large, and the door continues to rotate at the time of latch contact, the wheel B contacts the sliding surface K, and the sliding surface K moves around the connecting shaft Ck in the direction of the arrow D in FIG. Wheel B while rotating in the direction
In the state diagram in contact with b, the link AA rotates in the direction opposite to the arrow e in the figure, and the push spring U contracts. The sliding surface K is simultaneously subjected to the “force acting in the direction of closing the door” by the wheel B and the force “in the direction opposite to the closing direction” by the push spring U, and in the drawing around the pivot axis O of the connecting shaft Ck. Revolution of arrow b is suppressed and the door is decelerated.
As the door inertia force increases, the rotation of the sliding surface K is delayed with respect to the rotation of the door, the link AA further rotates, and the resistance of the movement of the wheel B in the direction indicated by the arrow C in FIG.

FIGS. 17 and 18 are examples illustrating that the link device continues to operate with the door stopped, regardless of the position of the connecting shaft of the sliding pair, which is not limited to the “mounting shaft of the opening / closing body and the expansion / contraction section”. is there. As in FIGS. 2C and 2D, the rotating body J is located far from the pivot axis O, and the operating region remains in an elongated region slightly separated from the door surface. It rotates greatly in the “switching range” and the door is sealed by “a large rotation far from the pivot axis O”.
Is a structure that can continue to rotate.
FIG. 17 is a link device in which the expansion / contraction part is composed of two links J and A. The link A is attached to the fixed support shaft Sw that fixes one side to the door frame W, and the other is attached to the rotating body J via the wheels B. The wheel B is a slider that moves along the sliding surface K, and the sliding surface K is “the inner surface on the side far from the pivot O of the long hole provided in the rotating body J”. The rotating body J is rotatably supported around a connecting shaft C provided on the door D and rotates in the direction of arrow A in the figure to rotate the door D in the direction of arrow B in the figure. Link
A compressive force acts on A. Illustration of the urging means for the telescopic part is omitted.
The wheel B is movable in the direction of arrow C in the figure where the “intersection angle Θak between the sliding surface K and the axis A Za of the link A” becomes an obtuse angle, and the range “(A)” shown in FIG. Is the tip K of the sliding surface K
The wheel B stays at the tip K when the crossing angle Θa is a right angle as shown in FIG.
Leave e. When the wheel B leaves the front end Ke, the rotating body J rotates greatly in the direction of the arrow a in the “switching range” as shown in FIG. FIG. 17C shows a state where the sliding surface KK attached to the rotating body J moves along the wheel BB attached to the door frame W. FIG.
(D) shows the state at the time of sealing when attaching wheel BB to door frame W so that movement is possible.
As shown in FIG. 17 (b), the acting force distance Lo is minimized just before closing and the door is substantially stationary. As the wheel B is locked at a position closer to the rotation axis C of the rotating body J, the rotating body J and the door do not interlock,
The rotating body J rotates while the door is kept stationary. The link device continues to move while the door is stopped at the time of latch contact, and the “force acting on the door” increases.

The structure of the embodiment shown in FIG. 18 is similar to FIG. 17 in that the wheel BB, which is the connecting shaft between the link A and the rotating body J, can move in the elongated hole Hj when the door is at a stationary position. And the door can keep rotating.
In FIG. 18, the wheel BB moves along the sliding surface K on the inner side surface near the door D of the long hole Hj provided in the rotating body J, and the sliding surface K includes the start end portion K1, the straight portion K2, and the end portion K3. Consists of
One of the links A is attached to the connecting shaft C of the door D, and the other is attached to the rotating body J via the wheels B. The rotating body J is rotatably supported around the fixed support shaft Sw of the door frame W. Rotating body J rotates in the direction of arrow A in the figure to rotate door D in the direction of arrow B in the figure. A tensile force acts on the link A. Illustration of the urging means for the telescopic part is omitted.
As shown in FIGS. 18 (a) and 18 (b), the wheel BB stays at the starting end K1 in the “range (A)”. As shown in FIG. 18 (c), the axial center line of the link A and the straight line portion K2 at the position D10 where the sealing operation starts.
As shown in FIG. 18 (d), when the position 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 is shown by an arrow on the straight line portion K2. It starts to move in the direction C, moves away from the recess K1, and moves to the terminal end 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.

The connecting shaft C is attached to “a rotating body Jc that is rotatably supported around the connecting shaft Cj provided on the door D”. A wheel BB is mounted on the rotating body Jc, and the rotating body J is urged by a pressing spring U in the direction of arrow D in the figure. When the rotating body Jc rotates in the direction opposite to the arrow D in the drawing and closes the push spring U to approach the door D, the wheel BB moves away from the pivot O. The sliding surface KK is an arc centered on the pivot axis O. When the wheel BB moves away from the pivot axis O, the wheel BB moves along the sliding surface KK, and the traction force of the link A is supported by the door D and the sliding surface KK. And the door is slowed down. When the wheel BB decelerates on the sliding surface KK, the push spring U extends, whereby the wheel BB moves away from the sliding surface KK and the door accelerates.
When the door decelerates, the “force acting on the door” increases and the push spring U contracts, and when the door accelerates, the “force acting on the door” decreases and the push spring U extends, and the reduction device of FIG. When the door decelerates, the wheel BB moves away from the sliding surface KK to accelerate the door, and when the accelerating door accelerates, the wheel BB moves along the sliding surface KK to decelerate the door.

As shown in FIG. 18 (a), when the hand is released from the door, the maximum static frictional force is applied to the door, so the "force acting on the door" increases and the push spring U contracts, and when the door starts to move, The frictional force is changed to the kinetic frictional force, and the “force acting on the door” is reduced, and the push spring U is extended. When a push spring U having a weak force is employed, even when the hand is released from the fully opened position as shown in FIG. 18A, the push spring U does not extend until closing and the latch is in a contracted state. Abut. That is, the larger the closing start opening, the longer the wheel BB moves along the sliding surface KK, and the door is decelerated.
The acceleration when starting to move from a stop state where the speed is zero is larger than the acceleration after that, and the phenomenon in which the static inertia from the dynamic inertia or the dynamic inertia to the static inertia alternates is recognized even if the driving range is recognized at a low speed. Not allowed in the driving range. FIG. 18 shows the speed reduction means applied at the beginning of the rotation at low speed, not at the end of the rotation at high speed.

In the case of FIG. 18 as well, the push spring U is inserted between the first door and the door as in FIG. 10, and the length of the push spring U varies depending on the magnitude of the “force acting on the door”. As the force increases, the “force acting on the door” decreases, and the length of the push spring U increases. In the case of FIG. 18 as well, FIG.
As in the case of 0, the length of the push spring U changes significantly immediately after the start of closing, but the rotation range where the door accelerates greatly is small, and the “force acting on the door” is air resistance and kinetic friction around the pivot O The resistance is balanced and the acceleration of the door is small so that it is constant and a large difference in the length of the push spring U is not recognized.
Depending on the opening degree of closing, “the magnitude of the door inertia force and the rotation speed of the door just before closing” varies greatly, but “the magnitude of the door inertia force and the rotation speed of the door just before closing” is determined by the length of the spring, It is difficult to change the magnitude of the braking force by changing the length of the pressing spring U. FIG. 18 shows a speed reduction means in which the length of the “distance where the braking force acts” changes depending on the length of the “door movement is calm”, and corresponds to the magnitude of the door inertia force of different sizes. .

FIG. 19 shows a link mechanism in which two links of a link A and a rotating body J form a crank mechanism. The two links replace the tension spring V shown in FIGS. It is the same as a spring in that the distance between them can change.
FIG. 9 is an operation explanatory plan view of the switchgear in which the “switching means” operates with the rotation axis Sw of the link AA crossed by the axis A of the link A as in FIG. 8.
An opening / closing device that transmits the driving force Mv of the rotating body J in the direction indicated by the arrow A to the rotational force Mo in the direction indicated by the arrow B of the door D. The link that connects the connecting shaft C and the fixed support shaft Sw by three links. Device. FIG.
FIGS. 1A and 1B show a case where the rotating body J is pivotally supported on a fixed support shaft Sw provided on the door frame W. FIG.
9 (c) and 9 (d) show the case where the rotating body J is pivotally supported by the connecting shaft C.
The link A is provided with a connecting shaft PP at one end and a connecting shaft P at the other end, the rotating body J is connected by the connecting shaft P, and the swing link AA is connected by the connecting shaft PP. 19 (a) and 19 (b), a torsion spring UV is attached around the fixed support shaft Sw, biases the rotating body J, and a tensile force acts on the link A. 19 (c) and 19 (d), a torsion spring UV urges the rotating body J around the connection axis C, and a compressive force acts on the link A. The hits G1 and G2 are in contact with the swing link AA, and the rotation of the swing link AA in the direction opposite to the arrow C in the figure is the same as the swing link AA in the direction of the arrow C
Prevent the rotation of. The contact G1 comes into contact with the swing link AA to change the position of the connecting shaft PP to “(A)
”In the vicinity of the pivot axis O of the door. The swinging link AA is separated from G1 just before closing, rotates in the direction of the arrow C in the drawing, contacts with G2, and moves the position of the connecting shaft PP away from the door pivot O in “range (ii)”.

19 (a) and 19 (c) show the middle of the closing process with broken lines, the solid line shows the state just before closing, and the state immediately after the axial center line Za of the link A crosses the center of rotation of the swinging link AA, The beginning of the “switching means” is shown. In FIG. 19 (c), the axial center line Za100 of the link A indicated by a broken line crosses over the pivot O and shows a state in which the door D is urged in the direction opposite to the arrow B in the figure. The door is urged in the opening direction, and the door is pressed against “door door 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 connecting 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.
19B and 19D, the solid line indicates the closed state, and the middle of the process of opening the closed door is indicated by a 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 swing link AA again, that is, an initial state returning to “rotating means in the range of (A)”. FIG.
The opening angle Θd of the door when returning to the “rotating means in the range (A)” in the opening process in (b) is the opening angle of the door when switching to the “rotating means in the range (ii)” of the closing process. Θ
Larger than d.
In the closed state shown by the solid lines in FIGS. 19B and 19D, the axial force acting on the link A becomes infinite as the axial center line of the link A and the rotating body J approaches a straight line. Get closer.

The rotating body Jsw shown in FIGS. 19C and 19D is rotatably supported around a fixed support shaft Sww provided on the door frame W, and has a fixed support shaft Sw at the tip portion to move the fixed support shaft Sw. The first door described in FIG. 10 is attached not to the door D but to the door frame W. The rotating body Jsw is urged around the fixed support shaft Sww by a pressing spring U in the direction opposite to the arrow D in the figure, and the rotation of the rotating body Jsw in the direction opposite to the arrow D is prevented by Gj. Door D and door frame W
Is an opening / closing body that rotates relative to each other while sharing the pivot axis O. If the door frame W is viewed from the door on the assumption that the door remains, the door frame W is rotating. In FIG. 19C and FIG. 19D, “force acting on the door frame” is transmitted through the rotating body Jsw so that “force acting on the door” is transmitted through the first door. The first door in FIG. 10 and the rotating body Jsw in FIGS. 19C and 19D have the same effect on the rotation of the door, and the same effect is recognized when the first door is attached to the door or the door frame. It is done.

FIGS. 20 and 21 are link devices in which the number of links is 5 and a pair is connected. As in FIG. 19, adjacent links are disengaged in the “switching range”. As shown in FIG. 19, the connecting shaft between adjacent links is not an “attachment shaft between the opening / closing body and the expansion / contraction part”, and is an embodiment of the link device that continues to operate with the door stopped. A link device with 5 links can move even if the number of links is reduced by one.
The “switching means” moves regardless of whether or not the door rotates with a structure in which the “switching means” is not interlocked with the door. Also, the door does not rotate due to the movement of the “switching means”.
If the operation is continued with the “direction of the force acting on the door” directed toward the axis O, the door and the expansion / contraction part all stop the link device, but the direction of the “force acting on the door” just before closing. The sealing operation is simultaneously performed while maintaining the state where the door is directed toward the pivot axis O of the door, and the “switching means” is started by temporarily stopping the door just before closing.
Do not use a speed reducer with resistance.
Similar to FIGS. 2 (c) and 2 (d), the operating area remains in an elongated area slightly away from the door surface,
The rotating body J is at a position far from the pivot axis O and rotates greatly in the “switching range”, and the door is sealed by “a large rotation at a position far from the pivot axis O”. 20 and 21 are “rotating mechanisms having an action point close to the pivot axis O and an action point far from the axis O”, and the device at the time of closing can be accommodated in a case that is elongated along the door frame W and does not protrude from the door surface. To contribute.
In the link device of FIG. 20, the link A of FIG. 19 is replaced with “a continuous body in which two links A and AA are connected in series”, and the link device of FIG. 21 has a link AA in parallel with the rotating body J of FIG. It is something to attach.

In the embodiment shown in FIG. 20, the link A connects the fixed support shaft Sw of 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”. The rotation of the rotator J in the direction of arrow A in the figure is transmitted to the door D.
FIG. 20 (a) shows the middle of the closing process with a broken line, and the solid line shows the state when the axial center line Za of the link A crosses the center of rotation of the link AA before the closing dimension. In the middle of the closing process, the link A and the link AA keep a straight line and pull the door, but the link A comes into contact with the rotating body J just before the closing, and the rotating body J overlaps with it. The link A and the rotating body J are relatively integrated and continue to rotate. The “wheel B mounted on the connecting shaft P” presses the sliding surface K provided on the door frame W, and the door is sealed.
If the lengths of the link A and the rotating body J are the same, and the positions of the connecting shaft P and the connecting shaft C coincide with each other, the link AA is stationary, and the door is sealed while keeping the “force acting on the door” constant. Will do. If the length of the link A is made slightly longer than that of the rotating body J so that the positions of the connecting shaft P and the connecting shaft C do not coincide with each other, the link AA pulls the door in the direction of pulling the door toward the pivot O, and the “door The door is sealed while increasing the "stopping force".

The rotating device shown in FIG. 21 includes a “rotating body J that is rotatably supported around a connecting shaft C” and a “fixed supporting shaft S”.
The link A, which is pivotally supported around w, is connected by the connecting shaft P, and the connecting shaft P pulls the link A by the rotation of the rotating body. As shown in FIG. Rotating in the “(A) range” on the fully open side, with the straight line T passing through the pivot O and the fixed support shaft Sw as the boundary, the door is closed in the “(A) range” on the fully closed side. Rotate in the opening direction.
The link AA and the support shaft Sa provided with the door are connected by a “connecting body in which the string s and the tension spring V1 are connected”, and the string S moves along the pulley BK. In this way, a long spring can be employed for a large movement of the expansion / contraction part, and the expansion / contraction amount of the spring is reduced. The cross section of the string S is crushed when the string S moves along the pulley BK, and returns when the string S does not move along the pulley BK.
By repeating the deformation and return, the “movement of the string S along the pulley BK” is decelerated.
FIG. 21B is a state diagram immediately before closing, and when the axis A Za of the link A coincides with the straight line T, the link device does not move at all while the link A pulls the pivot O.
When the “direction of the line of force acting on the door” moves toward the pivot axis O, the rotational resistance around the pivot axis O increases and the door decelerates. In the case of FIGS. 17 and 18, the door is pulled in the direction away from the pivot axis O, the gap between the latch male part Rd and the female part Rw is narrowed, and the resistance of the latch is increased. Further, the upper part of the door is tilted away from the pivot O and the lower part of the door is closer to the pivot O, and the wear of the pivot O is promoted in the same direction as the tilt due to its own weight. On the other hand, in the case of FIGS. 20 and 21, the door is pulled in the direction approaching the pivot axis O, the gap between the latch male part Rd and the female part Rw is increased, and the resistance of the latch is reduced. Further, the rotational resistance around the pivot axis O is decreased in the direction opposite to the inclination due to its own weight. Does not promote wear of the pivot O.

In the sealing device of FIG. 21, the link AA is rotatably supported around the “rotary axis Ia provided on the rotating body J”, and the rotating axis Ia crosses the axial axis Zv of the spring by the rotation of the rotating body J. The wheel B moves along the sliding surface K so that the AA rotates away from the Gaa and rotates in the direction of the arrow C in the figure.
The sliding surface K is rotatably supported around a rotation axis Ik provided on the door frame W and is urged in the direction indicated by the arrow D by a pressing spring U. The contact Gk prevents the sliding surface K from rotating in the direction opposite to the arrow D in the figure, and contacts the door frame W when sealed.
FIG. 21C is a state diagram at the time of sealing. When the link AA is rotated away from Gaa and the wheel B moves along the sliding surface K, the sliding surface according to the magnitude of the door inertia force. K rotates around the rotation axis Ik in the direction indicated by the arrow D in the figure, and “the wheel B at the intersection angle between the sliding surface K and the axis Aa of the link AA.
The angle Θak on the side where the wheel moves is reduced, and the wheel B becomes difficult to move on the sliding surface K. Thus, the sliding surface K inclined by the door inertia force increases the upward gradient with respect to the moving direction of the wheel B to stop the movement of the wheel B, but when the door inertia force disappears, the sliding surface K becomes It rotates around the rotation axis Ik in the direction opposite to the arrow D in the figure and tries to rotate it in the direction to open the door, but the wheel B overcomes this and rotates in the direction of the arrow C in the figure.
As the wheel B rotates in the direction indicated by the arrow C in the figure, the “intersection angle Θak between the sliding surface K and the axial center line Zaa of the link AA” gradually approaches a right angle. ”And the axial center line Zaa of the link AA are brought into a state of matching. This makes it easier for the wheel B to move on the sliding surface K, and at the same time, the “distance Lb between the action line Fb and the rotation axis Ib” becomes smaller, as described in FIG. The rotational force Mi "acting around the rotational axis Ib is largely converted into a sealing force Fb. In both FIG. 1 and FIG. 21, the wheel B revolves with a small force in the circumferential direction of “revolution C”, and the link AA supports a large radial force of “revolution C”. That is, the door is sealed with a very small force.

When the wheel B attached to the tip of the link A moves while pressing the sliding surface K, the pressing force Fb
The wheel B revolves with a small force around the rotation axis of the link A and supports a large force in the axial direction of the link A as the line of action and the axis A Za of the link A become closer to a straight line. Similar to the mechanism in which the door is sealed with a very small force, the connection axis P becomes “the link opposite to the connection axis P” as the axial center line Za of the two links connected by the connection axis P approaches a straight line. Revolves around the axis of rotation with a small force and supports a large force in the axial direction of the link.
FIG. 22 is a link device in which the expansion / contraction part is composed of two links of the link A and the rotating body J, and the opening / closing device that presses the door strongly in a straight line from the state where the shaft cores of the rotating body J and the link A are bent when sealed. FIG. 22 is a plan view of the operation of the opening / closing device shown in FIG. 22 with the first door Jc interposed between the expansion / contraction portion and the opening / closing portion as described in FIG. After stopping, the door D starts to close only by “the force of the push spring U interposed between the door D and the first door Jc”, and the “force acting on the door” before the latch contact Whatever your history,
Even if the door before the latch contact is rotating at a high speed, if the door substantially stops at the time of latch contact and the “force acting on the door” is approximately “the force to dent the latch”, the door slowly Explain that it is sealed.

One side Sa of the tension spring V is attached to the link A in the vicinity of the connecting shaft P, and the other Sw is attached to the rotating body J near the connecting shaft P. When the axis Zv of the spring is on the side close to the door frame W when viewed from the connecting shaft P, the door D
When the door D is on the side far from the door frame W, the door D rotates in the opening direction. FIG.
In a), it is on the side where the “intersection angle Θaj between the axis A Za of the link A and the axis Z Z of the rotating body J” is decreased, and the door is urged in the opening direction. FIG. 22A shows a fully open state in which the door D comes into contact with the door stop Gd90 and is stationary. As shown in FIG. 22 (b), when the axial center line Zv of the spring crosses the connecting axis P, the biasing direction of the spring changes to a direction for closing the door, and the door D rotates in the direction of arrow B in the figure. The broken line shown in FIG. 22 (c) moves along the operation of the connecting shaft P that moves along the "circular orbit Rsw centered on the fixed support shaft Sw" and the "circular orbit Ro about the pivot axis O". The operation of the connecting shaft C and the operation of each link in the closing process are shown. FIG. 22 (c) is a view of FIG.
d) is a state diagram at the time of sealing.

The driving force distance Lv decreases as the shaft cores of the rotating body J and the link A are bent from the bent state, and the driving force Mv around the connecting shaft P becomes “the link A working along the shaft core Za of the link A”. To the axial force Fa ". As the length of the link A is shorter than the length of the rotating body J, the link A rotates greatly while the door is slightly rotated, and the axial force Fa increases rapidly.
The “switching range” that does not involve any rotation of the door is represented by a boundary line between “(A) range” and “(A) range”. As shown in FIG. The “switching range” that hardly accompanies is represented by a range between “(A) range” and “(I) range”. In the opening / closing device of FIG. 22, the “force acting on the door” is largely switched before the latch contact, but the axial force Fa is the driving force distance.
It can be changed from zero to infinity in inverse proportion to Lv.
In FIG. 4, when the curvature is reduced at the base end portion Ko of the sliding surface K and a large force is applied at the time of sealing, the door can be moved within the range between “(A)” and “(I)”. The pressing force Fb is switched greatly with little rotation. Also in this case, the pressing force Fb is proportional to the acting force distance Lo.

“The door in which the first door Jc is interposed between the extendable part and the opening / closing part” is “the rotation mechanism in which the extension part rotates the first door Jc” and “the rotation mechanism in which the first door Jc rotates the opening / closing part. , And the former becomes a door as shown in FIGS. 1, 8, and 10. FIG. 22 simplifies the former structure. The door stops if no more force is applied at the time of latch contact, so the former is a rotation mechanism in which a large force is applied at the end of rotation.
Whatever the former, the door is operated by the latter rotation mechanism, and the movement of the door varies depending on the history of the force acting on the push spring U. If the sum of the force accumulated in the push spring U and the door inertia force at the time of latch contact is equal to or greater than the “force to dent the latch”, the door is fully closed without stopping. In order to stop once when the latch abuts and then close, the sum of the force accumulated in the push spring U and the inertial force of the door is equal to or less than the “force that causes the latch to be depressed”, and more than that thereafter. It will be.

A history of force acting on the push spring U will be described. When the door stops or decelerates, the push spring U contracts and accumulates force. When the door moves or accelerates, the push spring U loosens and transmits the force to the door. When the door is released, the push spring U contracts while the door is stopped, and the force acting on the push spring U reaches the “maximum static frictional force around the pivot axis O”. At the same time, the door starts moving and the push spring U loosens. It will be. A moving frictional force smaller than the maximum static frictional force acts on the door that has started to move, and a force greater than the moving frictional force accelerates the door. At the beginning of the door movement, the door repeatedly accelerates and decelerates and moves slowly.
As the door inertia force increases, the “force required to move the door” decreases and the push spring U loosens. Therefore, the force stored in the push spring U decreases as the push spring U contracts, and the latch spring comes into contact. "
It will be less than “the force to dent the latch”. When the door inertia force is large, the door is fully closed without stopping. If it is smaller, the door stops at the same time as the latch abuts against the door frame W.
Even when the door inertia force is not large, when the door receives a large amount of air resistance just before closing, and the door decelerates, the force stored in the push spring U contracts to “the force that can dent the latch”. When the door is stopped at the time of latch contact and the air resistance is lost, the push spring U starts to extend and the door is closed. In this case, even if the “rotating mechanism in which the extendable part rotates the first door Jc” is completely stopped, the door is sealed only by the “rotating mechanism in which the first door Jc rotates the opening / closing part”. When the force stored in the push spring U at the time of latch contact is smaller than the “force enough to dent the latch”, the “rotating mechanism that causes the telescopic portion to rotate the first door Jc” does not stop, and the push spring U It needs to move until the stored force is greater than “the force to dent the latch”.

As shown in FIG. 22C, the stop position of the “rotating mechanism in which the expansion / contraction part rotates the first door Jc” prevents “rotation in the direction indicated by the arrow a in FIG. However, it is adjusted by the hit Ga.
Designed so that the door D can be sealed with only the force of the contracted push spring U, both when the "rotation of the link A about the connecting shaft P" is prevented before and after the latch contact. Is done.
When blocking before the latch contact, the door D can be sealed only by the force of the push spring U contracted before the latch contact. When blocking after the latch contact, when the latch contact Thereafter, the door D can be sealed only by the force of the pressing spring U contracted. In any case, when the movement of the rotating body J and the link A stops with the latch being in contact, the door D is in a stopped state while the contracted push spring U is extended, and the press that has been contracted since the latch contact is made. Sealing is delayed by the time that the spring U extends.
“The force acting on the door” needs to be maximum when the latch comes into contact, and when the latch is recessed as shown in FIGS. 5C and 5D, it fits into the recess of the door frame facing the latch. It ’s almost no need. Regardless of the time before and after the latch contact, the position where the latch starts to be depressed is a position that prevents the “rotation about the connecting axis P of the link A” and the length of the push spring U becomes a natural length. The door stops rotating at the fully extended position. Depending on the position where the rotation of the door stops, there is a case where the sealing does not occur. This is because “the position where the rotating core J and the link A are locked in a bent state and the natural length of the push spring U. Means that it is possible to stop the door at a position where the sealing does not occur, and it is possible to stop the door at the same time as the sealing is reached.
In this way, by adjusting the contact Ga, the door can be stopped at a position where the impact sound is not generated at a position where the door does not hit the door by fitting into the concave portion of the door frame facing the latch. Or you can stop the door at a position close to it. Alternatively, the position for stopping the door and the force for sealing the door can be adjusted by the push spring UU.
Further, by adjusting the amount of contraction of the push spring U at the time of sealing, the force for sealing the door can be adjusted, and the magnitude of the impact sound and the force for opening the door can be reduced.

FIG. 23 is a plan view for explaining the operation of the switchgear which is a four-joint rotation mechanism in which the expansion / contraction part is composed of two links of the link A and the rotating body J as in FIG. It is. In addition to the releasable restraining means, means for preventing the restraining means from being released is provided to ensure that the "switching means" starts after the latch contact.
The broken line shown in FIG. 23A is an operation explanatory diagram of “range (A)”, and the solid line shows the state of the door D100 that is stationary when fully opened. The rotating body J is rotatably supported around the fixed support shaft Sw and is connected to the link A and the connecting shaft P. In the rotating body J, the connecting shaft P revolves around the fixed support shaft Sw by the driving force Mv in the direction of arrow A in the figure. A link A is connected to the connecting shaft P, and the link A is rotatably supported around the connecting shaft C. The connecting shaft C is movably attached to the door D via the rotating body Jc, and the four-node rotating mechanism is a five-node rotating mechanism. First, each of the connecting shaft C and the fixed support shaft Sw is the door D and the door frame. The operation of the four-bar rotation mechanism fixed to W will be described.

As shown in FIG. 23 (a), the “angle Θaj between the two links” remains in a state where it is bent to some extent from the time of full opening until just before closing, but the axis of the rotating body J and the link A is bent. In the process of shifting from the state to a straight line, the angle Θaj suddenly increases immediately before closing as shown in FIGS. The longer one of the two links is made shorter and the other is shortened, the longer the smaller link rotates while the shorter link rotates, and the force acting in the axial direction of the shorter link suddenly changes greatly. . Further, the distance between the mounting shafts Sw, C at both ends of the extendable portion is small, and the door rotation angle is also small. The “range of (i)” becomes very narrow, and the “force acting on the door” increases rapidly with a slight rotation of the door just before closing.
As shown in FIG. 23 (b), when the axis J of the rotating body J and the link A is about to be arranged in a straight line, the latch is about to begin to be depressed, ”Is insufficient to continue the rotation of the door, and at the same time insufficient to continue the rotation of the longer link. This lack of force temporarily stops the door just before closing.

As shown in FIG. 23C, the product of the axial force Fa acting along the axial line Za of the link A and the “distance between the acting line of the axial force Fa and the fixed support shaft Sw” is the fixed support shaft. In balance with the rotational force Mj acting around Sw, the rotational force Mj is largely converted into the axial force Fa. The same applies to FIG. 23C, and the product of the axial force Fa acting along the axial core line Za of the link A and the “distance Lv between the acting line of the axial force Fa and the connecting axis C” is The rotational force Mj acting around the connecting shaft C is balanced, and the rotational force Mj is largely converted into the axial force Fa even if it is small. In FIG. 1, when the wheel B presses the sliding surface K and seals the door, the “force Fb that the wheel presses the sliding surface” is large even if the force acting in the circumferential direction of the circular motion of the wheel B is small. In the same way as when the door is firmly attached to the door stop Gd, the link A
The force acting in the circumferential direction of the circular motion of the connecting shaft P when the axial line Za of the shaft and the “line of action of the force acting on the connecting shaft that moves circularly on the opposite side of the rotation axis of the link A” are arranged in a straight line. Even if it is small, a large force Fa is generated in the axial direction of the link A.
In this way, the door D and the door frame W are connected by “two links A and J having different lengths”, and the attachment shafts at both ends of the two links A and J move away as they are closed. Before the “switching range”, the two links A and J are bent and the “force acting on the door” is constrained to be small, and the “switching range” is released and the two links A and J are bent and the door is almost Make a straight line in an instant without rotating. While the door is slightly rotated in the “switching range”, the link device operates greatly, and the “force acting on the door” is switched from the insufficient force state to the strong force.

Next, the operation of the connecting shaft C will be described with respect to a five-bar rotation mechanism that is movably attached to the door D via the rotating body Jc.
The attachment axis C of the link A and the door D is provided at the tip of the “rotary body Jc rotatably supported around the connection axis Cj provided by the door”. The attachment shaft C can rotate around the connection shaft Cj. A push spring U is attached around the connection axis Cj, and as shown in FIG.
Then, the door is closed while the push spring U is contracted. As shown by the solid line in FIG. 23B, the rotation of the rotating body J remains stopped by “means for preventing release of the restraining means”.
As shown by the broken line in (b), the link A and the door D move as the compressed spring U expands to rotate the door.
The link AA is rotatably supported around a rotation axis Ia provided on the door frame W, and is urged by a pulling spring V in the direction of arrow D in the figure. A wheel B is attached to the tip of the link AA, and FIG.
) To (b), in the process of closing from the fully opened state, the wheel B presses the sliding surface K while moving along the sliding surface K of the recess provided on the side surface of the rotating body J. The rotating body J rotates about the fixed support shaft Sw in the direction of the arrow A in the figure, and the connecting shaft P moves on a circumference Rsw centered on the fixed support shaft Sw. As shown in FIG. 23B, the “sliding surface KK attached to the door D” closes the path of the wheel B just before closing, “movement along the wheel B sliding surface K” and “on the circumference Rsw of the connecting shaft P”. Movement "is stopped. The force Fb that the wheel B presses the sliding surface KK works in the direction of closing the door, so the door does not stop. Further, with the connecting shaft P stopped on the circumference Rsw, the rotating body Jc is rotated in the direction opposite to the arrow C in the figure by the pressing spring U as indicated by the broken line in FIG.
c and door D continue to move. As shown in FIG. 23C, the “sliding surface KK attached to the door D” is excluded from the path of the wheel B at the position where the latch male part Rd contacts the female part Rw, and the wheel B becomes the sliding surface K. It can move along.

As shown in FIG. 23 (b), even if the door is temporarily stopped, the links J and A other than the door D can be moved by the compression spring U being contracted again by a small force of “(a) rotating means”. There. Further, as shown in FIG. 23 (b), the wheel B staying in the vicinity of the fixed support shaft Sw in the “(range)” moves to the far side in the “switching range” as shown in FIG. 23 (c). To do. Link AA shaft core wire
Za and “the force Fb that the wheel B presses the sliding surface K” are shifted in the overlapping direction, and the force for rotating the rotating body J is increased. At the same time, the gradient of the sliding surface K becomes smaller with respect to the direction of movement of the wheel B, and the state shifts to a state where it is easier to move. Thus, the rotating body J rotates without stopping and the door is sealed.
Thus, by adding the rotating body Jc to form a link device having five links, the rotating body J
Even if the rotation of the rotating body J stops before the axis A of the link A becomes a straight line, the link device can move, and the latch male part Rd can come into contact with the female part Rw to be in a standby state. Also, after the door stops at the time of latch contact, if the two links are in a straight line and "force to dent the latch" is applied, the door will always be fully closed with no inertial force, The magnitude of the impact sound can always be reduced.

FIG. 24 is a plan view for explaining the operation of the four-joint rotation mechanism composed of an expansion / contraction part in which two links of the two opening / closing bodies D and W, the link A, and the rotating body J are chained as in FIGS. In the case of FIGS. 22 and 23, the door is strongly pressed in a straight line from the state in which the shaft cores of the rotating body J and the link A are folded when sealed. In addition, the force becomes insufficient at the beginning when the straight line starts to be bent. In the case of FIG. 24, the door is folded from the straight state, and the door is strongly pressed. The latter is a straight line with two axial cores overlapping. It is the same in that the door is strongly pressed and strongly presses the door. In the case of FIG. 24, there is no shortage of force at the beginning of overlapping and straightening.
The link A and the rotating body J are connected by a connecting shaft P, the connecting shaft C of the connecting shaft opposite to the connecting shaft P of the link A is fixed to the door D, and the connecting shaft opposite to the connecting shaft P of the rotating body J is fixed. The support shaft Sw is attached to the door frame W.
A torsion spring UV is attached around the connection axis C, and the link A rotates around the connection axis C in the direction of arrow A in the figure. Further, a driving force Mv works around the connection axis C. One support shaft Sj of the torsion spring UV is fixed to the rotating body Jc, and the other support shaft Sa moves in a groove H provided in the link A. The groove H is a link A.
Is a groove that is continuous from a position close to the center of rotation C to a position far from the rotation center C, and the support shaft Sa is at a position Ho close to the center of rotation “range (A)” and far from the “switching range”. By moving away from He, the rotational force Mj around the connection axis C suddenly increases when sealed, and the lack of rotational force during sealing is compensated.

The connecting shaft C is movably attached to the door D via the rotating body Jc, and the fixed support shaft Sw is movably attached to the door frame W via the rotating body Jsw. The four-node rotating mechanism is a six-node rotating mechanism. First, connection axis C
The operation of the four-bar rotation mechanism in a state where the fixed support shaft Sw and the fixed support shaft Sw are fixed to the door frame W will be described.
FIG. 24A shows the middle of the closing process with a broken line, and the solid line shows the state when fully opened. FIG.
As shown in (a), in the process of closing from the fully opened state, the connecting shaft C moves on the circumference Ro with the pivot axis O as the center. The door D rotates about the pivot O in the direction of arrow B in the figure. The connecting shaft P hardly moves, stays in the vicinity of the pivot O in the “(range)”, and keeps the acting force distance Lo small.
As shown in FIG. 24B, when the link A and the rotating body J gradually shift to the overlapping state, the connecting shaft C hardly moves and the connecting shaft P is “circumference Rsw centered on the fixed support shaft Sw”. Move "Up".
The driving force Mv is largely converted into the axial force Fj, and at the same time, the axial force Fj gradually works at right angles to the “closed door surface D0”.

In the process of closing from the fully opened state, the link device is “the axis core line Za of the link A and the axis core line of the rotating body J.
It moves in the direction in which the “intersection angle Θaj with Zj” decreases, and the axial core line Za of the link A and the axial core line Zj of the rotating body J gradually shift to overlap. From the balance of moments around the connecting axis C, the greater the crossing angle Θaj is, the smaller the driving force Mv is converted into the axial force Fj acting on the axis Zj of the rotating body J.
Moreover, as the two links are overlapped and the crossing angle Θaj is reduced, the conversion is increased.
The arc Ra shown in FIG. 24 (b) indicates that the link A rotates when the connection axis C is fixed. “The trajectory of the connecting axis P at the tip of the link A. The arc Rj rotates with the fixed support shaft Sw fixed. When the body J rotates, it is “the locus of the connecting axis P at the tip of the rotating body J and the connecting shaft P at the tip of one link moves along the other locus. The closer the trajectory is, the less the change in the distance between the two rotating shafts is.
As the position of the center of rotation (C, Sw) coincides, the link A and the rotating body J rotate relatively much together with little or no rotation of the opening and closing body, and the connection is made. The axis P moves with a small force in the circumferential direction of the circular motion and exerts a large force in the radial direction.
In this way, in the four-joint rotation mechanism in which the door D and the door frame W are connected by “two links A and J having substantially the same length”, if the rotation axis approaches before the closing dimension, the connection axis P is changed to “ It is provided with a releasable restraining means that restrains in the vicinity of the pivot O in the range (A), releases the restraint in the switching range, and moves away from the pivot O, while the door is slightly rotated in the switching range Operates greatly and switches from weak to strong when closed.

Next, the operation of the 6-bar rotation mechanism will be described.
The connecting shaft C is provided on the rotating body Jc, and the rotating body Jc is provided around the connecting shaft Cj on which the door D is provided.
It swings between a position that abuts against G1 and a position that abuts against G2. The fixed support shaft Sw is provided on the rotating body Jsw, and the rotating body Jsw is urged around the fixed support shaft Sww provided with the door frame W by a push spring Usw in the direction of the arrow C in the drawing so as to be rotatably supported. The rotation of the rotating body Jsw in the direction of the arrow C is prevented by the hit Gsw.
While the axial force Fj acting on the rotating body J is small, the rotating body Jc is in contact with G2 and the rotating body Jsw is in contact with the contact Gsw. When the two links overlap and the axial force Fj acting on the rotating body J increases, the rotating body Jc comes into contact with the contact G1, the rotating body Jsw moves away from the contact Gsw, and the fixed support shaft Sw approaches the connecting shaft C.
As shown in FIG. 24 (b), when the link A and the rotating body J are relatively integrally rotated, the speed of the movement is changed by changing the form of the link device by changing the strength of the push spring Usw. Can be changed. As indicated by the solid line, when the positions of the centers of rotation (C, Sw) of the link A and the rotating body J substantially coincide with each other, the link A and the rotating body J can rotate with a small spring force.
In the state where the center of rotation (C, Sw) is separated, the rotation cannot be performed unless the spring force is large. When the push spring Usw is strengthened, a force shortage occurs at the beginning of the “switching range”, and the movement speed of the link device becomes slow.
Thus, by making the attachment shafts of the expansion / contraction parts A, J and the opening / closing bodies D, W movable to form a link device with six links, the form of the link device is changed between the rotating operation and the sealing operation,
The magnitude of the “force acting on the door” can be switched. In the “(A) range”, the form in which the strong force of the expansion / contraction part acts on the opening / closing body is kept small.

FIG. 25 is a plan view for explaining the operation of the mechanism for controlling the “force acting on the door” during the slight rotation of the door until the latch male part Rd contacts the female part Rw and is fully closed. The force required when the latch male part Rd comes into contact with the female part Rw is the maximum over the entire rotation range from the fully open to the fully closed state, and the latch male part Rd is on the sliding surface Rww of the female part Rw Little force is required to move to the fully closed position. If the "force acting on the door" rises within this rotation range and the door accelerates, the inertial force is proportional to the square of the speed, so the impact sound cannot be ignored even if the "sealed door speed" is small. It becomes size.
The opening / closing device of FIG. 25 has the same structure as that of the embodiment of FIG. 24 and connects the attachment shaft C provided on the door D and the attachment shaft Sw provided on the door frame W by two links J and A. So that a large sealing force is applied, and in the embodiment of FIG.
The door is decelerated while resisting the movement of the wheel B by the sliding surface K so as to block the passage.

FIG. 25A is a plan view for explaining a series of operations from fully open to fully closed, and illustrates the state of the link A at each time point. The connecting shaft C moves on the “circumference Ro around the pivot axis O” in the direction of the arrow B in the drawing while approaching the rotating shaft Sw of the rotating body J, and “the connecting shaft P connecting the two links J and A”.
"Is biased by the pulling spring V and moves on the circumference Rsw centered on the fixed support shaft Sw in the direction of arrow A in the figure. When the two links J and A overlap before the closing, a large force acts in the axial direction of the two links J and A. At the same time, the two links J and A overlap and become relatively united. The two links J and A will work as levers. The driving force Mv acting around the fixed support shaft Sw increases as “the force acting on the door” increases as the operating point C approaches the support point Sw.
As the rotation axis C of the link A approaches the rotation axis Sw, the approach speed decreases, and the rotation axis C and the rotation axis Sw substantially coincide with each other just before closing. The link A bends in the middle, and the corner portion Ak moves circularly around the rotation axis C. As the center C of the circular movement approaches the rotation axis Sw, the approach speed decreases, and the locus of the corner portion Ak is the “switching range”. From a circular arc close to a straight line, “a circle centered on a substantially fixed spindle Sw”
become.

As shown in FIG. 25 (b), a wheel BB is attached to the corner portion Ak, and the wheel BB and the sliding surface KK are disengaged. The sliding surface KK is rotatably supported around a support shaft Skk provided on the door frame W, and is urged around the support shaft Skk by a push spring U in the direction of the arrow in the figure, and the arrow G in the figure by the contact Gk. Prevents direction rotation. The sliding surface KK is composed of a base end portion Ko of the linear portion and a terminal portion Ke that greatly changes the curvature, and when the wheel BB moves circularly, the wheel BB moves while pressing the sliding surface KK and the push spring U is contracted. In the middle of the movement of the wheel BB in the base end portion KKo, when the angle Θak is a right angle, the contracted push spring U starts to expand and the sliding surface KK presses and moves the wheel BB.
The sliding surface KK is the same as the first door described in FIG.
Mv is not transmitted to the door, but the driving force of the expansion / contraction part as if the door was rotated by the force of the push spring U
If the wheel BB is moved on the sliding surface KK until Mv is at a right angle Θak, the latch male R
When d moves on the sliding surface portion Rww of the female portion Rw, the door is rotated only by the force of the push spring U that urges the sliding surface KK, and the wheel BB slides as shown in FIG. 25 (c). When reaching the end portion KKe of the surface KK, the wheel BB presses the door D against the door stop Gd by the pressing force Fb acting in the circumferential direction of the circular motion.

As in the case of the push spring U shown in FIG. 12, the force of the pulling spring V is reduced, and the "(i) rotating means" must be increased accordingly, but this is the same as when the resistance of the latch is large. The push spring U absorbs the inertia force of the door while contracting, and the force stored in the push spring U works to close the door instead of pushing the door back. Finally, the door inertia force is converted into a sealing force.
The door inertia force acts in the circumferential direction of rotation of the sliding surface KK, and the force acting in the moving direction of the wheel BB is in the radial direction. Even if the pushing spring U is strengthened and a large door inertia force is received by the sliding surface KK, the wheel B
The influence of the push spring U on the moving speed of B is small. Further, even if the pressing spring U is strengthened, it does not rebound in the direction of opening the door. The push spring U absorbs the inertia force of the door and contracts, but the wheel BB slides on the sliding surface K.
Since it moves while pressing K, it is not restored and is not pushed back in the opening direction. The sliding surface KK simultaneously receives the pressing force Fb and the door inertia force in the opposite direction, and is sandwiched between two forces as in the sliding surface K2 shown in FIG. Surface KK
As with the force with which the wheel B2 shown in FIG. 12 presses the sliding surface K2, the force that presses the door simultaneously suppresses the reaction force of the door inertia force together with the door.

In FIG. 25, the urging means of the rotating body J indicates that when the latch male part Rd moves on the sliding surface part Rww of the female part Rw by the restoring force of the pushing spring U, the driving force Mv becomes invalid for the rotation of the door. It will be. In FIG. 25, the link AA is rotatably supported around a support shaft Ia provided on the rotating body J, is bent at a right angle in the middle, is provided with one support shaft Sa of a spring at each corner, and has a wheel at the tip. B is attached. The other support shaft Sww of the spring is provided on the door frame W.
As shown in FIG. 25 (a), the link AA rotates while the side surface is in contact with the fixed support shaft Sw in the "(A) range", and the spring support shaft Sa revolves around the fixed support shaft Sw slightly. .
The link AA and the tension spring V are “the coupling body of the tension spring V and the link AA” as in FIG.
The “continuous body AV of the tension spring V and the link A” in FIG.
25, the constraint is released. However, in FIG. 25, the constraint is not released when the axis A Zaa of the link A and the axis Zv of the spring are in a straight line. As shown in FIG. 25A, when the side surface of the link AA moves away from the fixed support shaft Sw, the wheel B moves along the sliding surface K1, and the spring support shaft Sa revolves around the fixed support shaft Sw slightly. to continue. When the latch is in contact with the wheel B, the sliding surface K
1 apart from 1, the spring support shaft Sa moves away from the fixed support shaft Sw, and the driving force Mv increases. 2
The restraint of the support shaft Sa of the spring is released with the two shaft core wires bent.

As shown in FIG. 25C, the outer edge of the sliding surface K3 is “an arc centered on the fixed support shaft Sww, and the length of the tension spring V changes when the wheel B moves along the sliding surface K3. The pulling force of the pulling spring V does not act on the door, and the force of the pressing spring U is a rotating body only at the moment when the wheel B moves away from the sliding surface K1 and becomes straight from the bent state of the two shaft cores. Acts on J but latch male part R
When d moves on the sliding surface portion Rww of the female portion Rw, it becomes invalid thereafter.
As shown in FIG. 25 (b), the sliding surface K3 is supported by a fixed support shaft Sk provided on the door frame W, and the sliding surface K3 can be fixed at a predetermined rotation angle. Moves in the direction indicated by the arrow D in the figure around the fixed support shaft Sk and arc Rsww
If it is along 1, resistance is applied to the movement of the wheel B in the direction of arrow E in the figure, and the door decelerates when sealed. The door accelerates along the arc Rsww2.
As described above, since the rotating body J rotates greatly with respect to the small rotation of the door D, the “force acting on the door” can be freely operated in the large rotation range of the rotating body J. When the door D comes into contact with the door contact Gd, the “force acting on the door” does not work, and the spring force of the latch male part Rd causes the impact sound to be fitted into the female part Rw. Becomes the smallest.
The means applied when the door D abuts against the door stop Gd is the most effective for minimizing the impact sound, and the last applied means no matter how effective the means applied so far works. If is not effective, the impact sound will not be reduced.

In FIGS. 26 and 27, one link is added to the four-bar rotation mechanism in which the expansion / contraction part of FIGS. 22 to 24 is composed of two links A and rotator J, and the expansion / contraction part is link A, rotator J, and link AA. FIG. 6 is a plan view for explaining the operation of the switchgear having a five-bar rotation mechanism composed of three links; In the “range (A)”, the link A and the link AA are aligned and operate as one link, and in the “(range)”, the link A and the rotating body J are relatively integrated. Operates as one link.
In FIGS. 8 and 19, the links attached to the opening / closing part abut against and separate from the opening / closing part, and adjacent links contact and separate from each other except for the attachment part of the opening / closing part and the expansion / contraction part. By adopting a five-bar rotation mechanism, a branch point is recognized in the process of movement of the link device, and it is divided into two forms, when the link device stops and when it continues.
In the opening / closing device described so far, the door is temporarily stopped when the latch comes into contact. However, the opening / closing device shown in FIGS. 26 and 27 allows the door to be stopped before the time when the latch comes into contact. Stops the door at an unopened position and prevents a finger jamming accident when hit by a strong wind.

The opening / closing device of FIGS. 26 and 27 is a link device of a five-bar rotation mechanism that connects the attachment shaft C provided on the door D and the attachment shaft Sw provided on the door frame W with three links J, A, AA. Instead of link A, “two links with link A and link AA connected by connecting shaft PP” are “fixed support shaft S
This is a structure connected to a connecting shaft C and a connecting shaft P provided at the tip of a rotating body J that is rotatably supported around w. The connecting shaft PP traverses the "straight line Tc passing through the fixed support shaft Sw and the connecting shaft C" twice and reciprocates. The axial center line Za of the link A is a straight line passing through the connecting shaft P and the connecting shaft PP, and the link device of FIG. 26 is configured such that the axial center line Za of the link A crosses the fixed support shaft Sw. The device is attached with a spring Vpp around the connecting shaft PP or around the connecting shaft C as shown in FIG. 27 so that the link A and the link AA are closed in the direction of the arrow D in the drawing centering on the connecting shaft PP. The connecting shaft PP reciprocates across the straight line Tc.

The link A of FIG. 26 has its tip bent into an L shape, and the link A of FIG. 27 has its tip not bent into an L shape. FIGS. 26 and 27 (a) are operation explanatory views before the connecting shaft PP crosses the “straight line Tc passing through the fixed support shaft Sw and the connecting shaft C”. Connecting points P, PP,
C is always on the same straight line ZZ, and the two links A and AA operate as one link, and the rotating body J rotates around the fixed support shaft Sw by an urging means (not shown) in the direction of the arrow A When rotating, the door D is pulled through the two links A and AA and rotates about the pivot O in the direction of arrow B in the figure. In the case of FIG. 27, the spring Vpp is stretched by the force that the rotating body J pulls the link A in the “range (A)”, and the link A and the link AA are in a straight line. The force is weakened, the link A and the link AA are closed in the direction of the arrow D in the figure around the connection axis PP, and the link A and the link AA are operated as one link while being folded.

In the "(A) range" where the two links J and A are not engaged, the connecting shaft P is "a straight line 1
While the two links A and AA are pulled, the connecting shaft PP pulls the link AA in the “range (ii)” where the two links J and A are engaged. When the two links J and A are engaged, the two links J and A act as levers, and the fixed support shaft Sw becomes a lever support point and the connecting shaft PP becomes an action point.
In the “range (ii)”, the distance between the rotation center Sw and the action point PP becomes smaller than the “distance between the rotation center Sw and the action point P”. The working driving force Mv is greatly converted to “force acting on the door”.
Unlike the case where the swing link A in FIG. 8 is separated from the door D in the “switching range” and the restraint is released, FIG.
In the case of 6, 27, the two links J and A are engaged and restrained in the “switching range”. Even when the rotating body J rotates in the direction opposite to the arrow A in the figure, the same effect can be obtained if the direction in which the connecting shaft PP reciprocates is reversed.

When the connecting shaft PP crosses the “straight line Tc passing through the fixed support shaft Sw and the connecting shaft C”, the link A and the rotating body J come into contact with each other and are relatively integrated. 26 and 27 (b) show the connecting shaft P.
FIG. 10 is an operation explanatory view after P has reciprocated twice across a “straight line Tc passing through the fixed support shaft Sw and the connecting shaft C” twice.
The link A and the rotating body J are relatively integrated to form one link AJ, and one link A
J operates. The axis line Zaj of one link AJ is “a straight line passing through the fixed support shaft Sw and the connecting axis PP. When the connecting axis PP reciprocates and crosses the straight line Tc for the second time, the axis line Zaj and the axis line of the link A Zaa extends in a straight line from the bent state, and the “distance between the fixed support shaft Sw and the connecting shaft C” increases. It bends again from the linearly extended state, and the “distance between the fixed support shaft Sw and the connecting shaft C” decreases. Along with this, the door opens once and then closes again.
The amount of rotation that the door is once opened can be adjusted by the contact Ga, and the more the shaft core line Zaj and the shaft core line Zaa extend in a straight line until the two links J and A are engaged, the more the door cannot be opened.

Before the link A and the rotating body J are relatively integrated, the connecting shaft PP rotates about the fixed support shaft Sw in the direction indicated by the arrow C in the figure, and after being integrated, the connecting shaft PP rotates in the direction opposite to the arrow C in the figure. To do. Link A
Since the connecting shaft PP reverses the moving direction when the rotating body J and the rotating body J are relatively integrated, the “force acting on the door” instantaneously becomes zero, and the link A and the link AA are centered on the connecting shaft PP. Then, it rotates in the closing direction in the direction of arrow D in the figure.
When this rotation in the closing direction is prevented by the contact Ga, the door moves due to the rotation of one link AJ in the direction of arrow A in the figure, but it does not move even if the door is pushed and closed. This means that when the door rotates at a low speed, the door is closed by the driving force Mv, but when the door rotates rapidly and is closed by the door inertia force, the door is suddenly stopped.

27 (c) and 27 (d) show a link device having a structure in which the connecting shaft C is attached to the door D via the first door Jc. As shown in FIG. The first door Jc and the door D are closed in an open state, and when the link A and the rotating body J are relatively integrated just before the closing, the connecting shaft PP reverses the moving direction. “The first door Jc and the door D in the opened state” begin to close due to the door inertia force.
FIG. 27C shows a state in which the door rotates at a low speed and the door inertia force is small, and the first door Jc and the door D are open and the connecting shaft PP crosses the straight line Tc again. The door is closed without rotating in the opening direction. When the connecting shaft PP moves in the direction opposite to the arrow C in the figure, no load is applied other than extending the tension spring V attached around the connecting shaft PP, so the connecting shaft PP moves in the direction opposite to the arrow C in the figure. It ends in an instant.
The "switching means" of the present invention has a problem that the operation ends in an instant with no load, and measures are taken to reduce or seal the load applied to this operation, but in the first place the door does not move with a spring If an electric actuator that maintains a constant speed is used, the problem is solved all at once.
FIG. 27 (d) shows a case where the door rotates at a high speed and the door inertia force acts greatly, and the connecting shaft PP is a straight line Tc.
The first door Jc and the door D are in a closed state before crossing again, indicating a state in which the doors are relatively integrated and suddenly stop. When the door inertia force disappears after a lapse of time, the door once rotates in the opening direction and then closes.
By adding one link to the four-joint rotation mechanism in this way, the link device will show different forms for door inertia forces of different sizes, and braking force will act on the door inertia force. become.

When the door D rotates in the closing direction, the connecting shaft PP crosses the straight line Tc, and the link A and the rotating body J are relatively integrated, the rotating body J and the link A are in the closing direction around the connecting shaft P. Rotate. FIG.
When opening the door with the rotating body J and the link A closed as shown in FIGS. 6 and 27 (a), the link A, the rotating body J, and the connecting shaft P are relatively opened in the direction of opening. Rotate. FIG.
In the cases shown in a) and (b), when the door is opened, the link A and the link AA are in a straight line, and the link A and the rotary body J open around the connecting shaft P, while the rotary body J Rotate in the opposite direction. The door can be opened.
In the case shown in FIGS. 26A and 26B, when the door D rotates in the closing direction and the connecting shaft PP crosses the straight line Tc and the link A and the rotating body J are relatively integrated, the link A Since the shaft center line Za of the link A crosses the fixed support shaft Sw, the shaft core line Za of the link A once crossed cannot be returned. FIG.
6 (a) and 6 (b), when the axial center line Za of the link A and the “side surface where the link A and the rotating body J abut each other” are on the opposite sides with the fixed support shaft Sw in the middle The force in the direction of opening the door acting on the connecting shaft PP rotates the connecting shaft P in the closing direction of the door, and the link A and the rotating body J rotate in the direction in which they contact each other instead of being separated from each other. It will not open.

26 (c) to 26 (e) are explanatory views of a device that opens the door even when the axial center line Za of the link A once crosses, and the wheel B is mounted at a position different from the connecting shaft PP of the link A, The sliding surface K is rotatably supported around the fixed support shaft Sw, and the rotation in the direction indicated by the arrow E in the drawing is prevented by Gk. The sliding surface K has such a shape that the wheel B moves away from the fixed support shaft Sw when the wheel B moves from the proximal end Ko of the sliding surface K toward the terminal end Ke, and the wheel B is fitted to the terminal end Ke. A recessed portion is provided.
FIG. 26 (c) shows a state in which the axial center line Za of the link A has crossed for the first time.
When a force in the direction of opening the door is applied to P, it is in a position to rotate in the direction of arrow A in the figure. The wheel B engages with the proximal end Ko of the sliding surface K. FIG. 26 (d) shows a state of sealing, and the sliding surface K is in a state where the rotation in the direction of arrow E in FIG.
To the end portion Ke. When the connecting shaft PP moves around the fixed support shaft Sw in the direction opposite to the arrow C, not only a force for rotating the door in the opening direction is required, but also the rotating body J linked with the side surfaces is linked. A rotates in a direction that separates the opponent from each other, and the wheel B moves while expanding between the rotating body J and the link A. Therefore, a load is applied to the movement of the wheel B, and the connecting shaft PP instantaneously Move slowly without moving in the opposite direction. When the wheel B fits into the recess, the connecting shaft P is in a position that rotates in the direction opposite to the arrow A in FIG.
FIG. 26 (e) shows a state when the door is opened. While the wheel B is fitted in the recess, the sliding surface K moves away from Gk and rotates in the opposite direction to the arrow H in the drawing, The state where the wheel B escapes from the recess and the door opens is shown. The connecting shaft P is in the direction opposite to the arrow a in FIG.

FIG. 28 is a five-joint rotating mechanism shown in FIGS. 26 and 27, and there are three links J between the door D and the door frame W.
, A, AA, and a link device in which the side surface of the link A moves along the wheel B as the wheel BB of the corner portion Ak moves along the sliding surface KK in FIG. . FIG.
, 27 is added to the five-bar rotation mechanism shown in FIG. 27, and the link A and the link AA that are straight in the “(A) range” can be bent before the closing dimension. By approaching to the pivot axis O, the “force acting on the door” before the “switching means” is insufficient and the vehicle can be decelerated. .
The rotating body J is urged by the tension springs V1 and V2, and one of the supporting shafts is provided on the rotating body J.
The other is attached to the supporting shafts Sw1 and Sw2 provided on the door frame W on Sj1 and Sj2. The tension spring V1 works effectively in the “(range)” and the tension spring V2 works in the “(range)”. The rotating body J and the link A are connected by a connecting shaft P, and the link A and the link AA are connected by a connecting shaft PP. As shown in FIGS. 28A and 28B, the rotating shafts Sw and Swb of the rotating body J and the wheel B are provided on the “rotating body Jc rotatably supported by the fixed supporting shaft Sww”. The push spring U is urged to rotate in the direction opposite to the direction indicated by the arrow D in FIG. However, the movement of the link device does not stop.

FIG. 28C is a plan view for explaining a series of operations from fully open to fully closed, and illustrates the position of the link member at each time point. The connecting shaft C moves on the circumference Ro centering on the pivot axis O in the direction of arrow B in the figure, and the connecting shaft P moves on the circumference Rsw centering on the fixed support shaft Sw in the direction of arrow i in the figure.
The link A and the link AA are in a straight line for a while from the fully opened state, and when the side surface of the link A comes into contact with the wheel B, the link A and the link AA start to bend. In the state where the side surface of the link A is in contact with the wheel B, the lever with the connecting shaft P as the applied point and the connecting shaft PP as the operating point functions using the “contact point between the side surface of the link A and the wheel B” as a fulcrum. Even if the distance between the fulcrum action points decreases and the distance between the fulcrum application points increases, the axial center line Zaa of the link AA is the action line of the force that pulls the door, and the direction is directed to the axis O just before closing. The “force to rotate the door” is reduced. Even if the force acting on the applied point is large, the door acts small. When the side surface of the link A comes into contact with the wheel B, the connecting shaft PP approaches the wheel B after it begins to bend, and the wheel B moves along the side surface of the link A until the link AA is perpendicular to the “closed door surface D0”. It travels a long distance, but the door rotation during this time is small.

As shown in FIG. 28 (a), the latch male part Rd contacts the female part Rw, and the side surface of the link A is the wheel B.
When the connecting shaft PP approaches the wheel B and the latch male part Rd begins to be depressed as shown in FIG. 28B, the “switching means” operates greatly with respect to slight rotation of the door. It will be.
In the middle of the operation of the “switching means”, the tension spring V1 loses the force to rotate the rotating body J, and the axial center line Zv of the tension spring V2 gradually moves away from the center of rotation Sw of the rotating body J. The axis Zv is fixed spindle Sw
Is close to zero, the force for rotating the rotating body J is close to zero, and the wheel B is temporarily stopped. In this way, the drive unit moves slowly with little force to rotate the door just before closing. On the other hand, when the door rotates vigorously, as shown in FIG. 28B, the link AA rotates in the direction of the arrow C in the figure, and the rotating body J rotates in the direction of the arrow A in the figure, so that the drive unit rapidly For example, when the link A is formed by a leaf spring and is curved to strongly press the wheel B, the wheel B is rotated.
Link AA rotates in the opposite direction to the arrow C in the figure and the rotating body J
Rotates in the opposite direction to the arrow a in the figure and resists rotation in the closing direction of the door. In addition, FIG.
), The rotation axis Swb of the wheel B is rotatably supported around the fixed support shaft Sww and is urged in the direction opposite to the direction indicated by the arrow D in the figure by the push spring U. The link A, the rotating body J, and the rotating body Jc are relatively integrated with each other and the fixed support shaft Sww rotates in the direction opposite to the arrow C direction in the figure to resist the rotation in the closing direction of the door. I can do it.

When the movement of the wheel B is delayed with respect to the closing rotation of the door in this way, the “intersection angle Θaa between the door D surface and the axis Aa of the link AA” becomes a sharp acute angle, and inertia force acts on the door. Furthermore, the door is decelerated at an acute angle. In this way, inertial force can be converted into braking force. When the door is pushed strongly by hand or when a sudden force such as a gust of wind acts on the door, the door will rotate rapidly, but the greater these external forces, the greater the braking force and the sudden braking applied to the door. Become.
From the beginning of the “switching range”, the crossing angle Θaa begins to increase, and “the force that rotates the door” begins to increase. That is, the “switching means” accompanies the acceleration of the door. However, the crossing angle Θaa still tends to become sharper when an external force is applied.
As shown in FIG. 28C, when the axial center line Zaa of the link AA is brought close to the pivot axis O just before closing, the crossing angle Θa between the axial center line Za of the link A and the axial center line Zaa of the link AA is “the switching range”. It turns out that the crossing angle Θa has a minimum value in the middle.
As shown in FIG. 28A, when the contact Ga for limiting the crossing angle Θa is attached, the contact Ga is decoupled from the side surface of the link AA, thereby decelerating before the closing dimension, and the deceleration is released at the time of sealing.
The link A and the link AA are relatively pushed together when the door is strongly pushed by hand while the contact Ga is engaged with the side surface of the link AA or when a sudden force such as a gust of wind acts on the door. The rotation of the rotating body J in the direction of arrow A in the figure is reversed.

The link device of FIG. 22 restrains the rotation of the second connecting shaft so that the pivot O of the five-bar rotation mechanism is the first, and the door D is the first link, and the first door Jc is the second. In this case, the first link and the second link are disengaged. The link device of FIG. 28 is also a five-joint rotation mechanism, and when the contact Ga engages and disengages from the side surface of the link AA, the rotation of the third connecting shaft is releasably restrained. The third link is disengaged. Thus, when the five-bar rotation mechanism becomes the four-bar rotation mechanism, FIG.
25 and the link device of FIG. 28 are the same in that a friction means is provided on the first link, and one link of the movable four-bar rotation mechanism. By restraining, it is close to the state where it cannot move. This is the same as the case where the tension spring V is attached to the third connecting shaft of the five-joint rotation mechanism in FIGS.
As described above, the restraint or semi-restraint means can be provided around the connecting shaft of the link device to control the operation of the link device. However, the motion differs depending on the place of restraint and plays a different role. For example, in the 5-joint rotation mechanism shown in FIGS. 26A and 26B, the magnitude of the driving force Mv changes from small to large when the third link and the fourth link are disengaged. FIG.
If the sliding surface K is the fourth link, the door frame W is the fifth link, and FIG. 2 shows a state where the fifth connecting shaft is semi-constrained. The sliding surface K in FIG. 2 is the first door Jc in FIG. 22, and FIG. 2 shows that both the fifth connecting shaft and the second connecting shaft in FIG. They are the same and play the same role.

Since the link A acts as a lever and constantly presses the wheel B strongly, the frictional resistance acting around the rotation axis Swb of the wheel B is large, and the “movement of the link A along the wheel B” is braked. In FIG. 25, the wheel BB is mounted on the support shaft Skk provided on the door frame W, and the wheel BB is connected to each corner Ak of the link A.
When the position of the wheel BB and the sliding surface KK is changed so that the frictional resistance acts around the rotation axis Skk of the wheel BB, “the wheel BB at each corner Ak of the link A Brake the movement along. In FIG. 28, the door is further decelerated by attaching a delay device such as a damper around the rotation axis Swb of the wheel B or around the rotation axis Skk of the wheel BB in FIG. The closing device of the present invention does not apply a resistance directly to the door to delay the rotation of the door, but applies a resistance to the driving unit to indirectly delay the rotation of the door.

As the means to decelerate the door by directly applying resistance to the door either stops the rotation of the door or the speed reducing means does not work at all, delays the operation of the drive unit or "switching means" The use of a damper or friction resistance as a means will either stop the operation of the drive unit or "switching means" or not work at all because the drive unit or "switching means" operate with very little force Results in. The means for increasing the frictional resistance around the rotation axis Swb of the wheel B as shown in FIG.
This can be solved by increasing the “force acting on the door” to such an extent that the operation of the drive unit and “switching means” is not stopped. In this case, the “force acting on the door” does not interlock with the door, and can be set to a constant magnitude.
In this manner, the wheel B moves along the side surface of the link A over a long distance and takes a long time until the latch male part Rd comes into contact with the female part Rw and begins to be depressed. Disappear.

In the embodiment of FIG. 29, the time required for the “switching means” is delayed by shifting the plurality of operations described above from inertia to dynamic inertia. During this time, the movement of the expansion / contraction part is not transmitted to the opening / closing movement of the door, so that the door runs idle and the “force for rotating the door” is attenuated.
The "switching means" in FIG. 29 applies a "load that accumulates force in the sealing device" while rotating the door slightly or without rotating the door due to the continuous operation of many springs and multiple operations. The action of "means" is delayed, and "power stored in the sealing device" gradually grows
When the "force to seal the door" is reached, the sealing device is activated to seal the door. At this time, force acts on the door without excess or deficiency, and the door is sealed. Since the impact sound at the time of sealing is proportional to the magnitude of the extra force, the impact sound at the time of sealing becomes the smallest.

FIG. 29 (a) is “range (A)”, and the wheel B attached to the door D moves “on the circumference Ro around the pivot axis O in the direction indicated by the arrow C in the figure, and the door D pivots. A series of operations that rotate in the direction of the arrow B in the figure is described about the axis O. The sliding surface K is urged in the direction of the arrow A in the figure about the rotation axis Ik by the pulling springs V1 and V2, and the wheel B Rotate while pressing.
The shape of the sliding surface K is designed according to the drawing method shown in FIG. 4 (c) so that the distance between the "operation line of the force Fb that the wheel presses the sliding surface" and the pivot axis O is substantially constant. In addition, a small force acts on the door in the “(A) range”.
The “rotation mechanism in which the wheel moves along the sliding surface” means that the “wheel moves along the sliding surface” no matter how large the “force Fb (ie, the force acting in the radial direction of rotation) of the wheel pressing the sliding surface”. The force to be moved (that is, the force acting in the radial direction of rotation) has a feature that can be reduced as much as possible by reducing the distance between the "operation line of the force Fb that the wheel presses the sliding surface" and the pivot O, When this feature is used for a door, no matter how strong a spring is used, it does not affect the opening and closing of the door.

In the case of FIG. 29, since the operation of the “switching means” is large and plural, the spring needs to be expanded and contracted greatly. Therefore, the spring force acts greatly in the “range (A)”. In addition, since the number of parts increases and the number of connecting parts connected by sliding pairs or turning pairs increases, the frictional resistance of the entire apparatus increases and a strong spring must be used. By adopting the “rotating mechanism in which the wheel moves along the sliding surface”, the force of the strong spring is “(A) as shown in FIG.
It is preserved in the “range” and works little on the door, and acts on the door greatly in the “range” as shown in FIGS. 29 (b) and 29 (c).
The spring force attenuates as the "switching means" progresses, but the device must move to a state where it can move more easily even with a small force, and at the same time, it must act on the door with a small force. As recognized in many embodiments, the means for enabling the drive shaft to move in the “switching means” and the means for allowing the sliding surface K to rotate increase the operation of the “switching means” and “force acting on the door”. ”Increases the expansion and contraction of the spring until reaching the force that seals the door, resulting in a decrease in the rigidity of the spring, and the“ force acting on the door so that the wheel B is loose and has a long gradient ” Is to grow slowly.
As shown in FIG. 29 (a), in the “range (A)”, the wheel B moves greatly along the sliding surface K from the terminal end Ke to the base end Ko, but the direction in which the line of action of the force Fb is directed. Is substantially constant with respect to the pivot axis O, and the rotation of the sliding surface K rotating around the rotation axis Ik in the direction of arrow A in the drawing is small. That is, the rotation of the closing device is small and the rotation of the door is large. In the “range (ii)”, the wheel B stays in the vicinity of the base end portion Ko and moves little, but the direction in which the line of action of the force Fb faces greatly rotates. FIG. 29 (b) (
As shown in c), the rotation of the sliding surface K that rotates about the rotation axis Ik in the direction of arrow A in the figure is large.
That is, the rotation of the closing device is large and the rotation of the door is small.

The rotation axis Ik of the sliding surface K is provided at the tip of the shaft Sh, and the shaft Sh is a rotating body Jsw.
It moves along with the groove | channel H provided in this. The rotating body Jsw is rotatably supported around a fixed support shaft Sw provided on the door frame W, and the rotation in the direction indicated by the arrow D in the figure is controlled by a wheel BB attached to the end of the shaft Sh. As shown in FIG. 29 (a), in the "(A) range" where the force for rotating the door is weak, the shaft Sh is pulled in the direction of the arrow in the drawing by the pulling springs V1 and V2, and is pulled out by the contact Gjc. So that
When the wheel B approaches the base end portion Ko of the sliding surface K just before closing, as shown in FIG.
The forward passage (in the direction of arrow H in the figure) is blocked in front of the passage of the wheel B. FIG.
In the state shown in (b), the shaft Sh moves backward and the sliding surface K rotates around the wheel B in the direction indicated by the arrow G in the figure. At the same time, the wheel BB moves from the sliding surface KK1 to KK2 and descends the step.
In this way, the rotating body Jc rotates in the direction indicated by the arrow D in the drawing to seal the door as shown in FIG.
The “(i) rotating means” includes an operation in which the shaft Sh moves backward and rotates, and an operation in which the sliding surface K rotates. Rotating means "
The operation time is delayed.

The wheel B is mounted on a rotation axis Ib of a wheel provided on the link A, and the link A is rotatably supported around a connection axis C provided on the door D. The push spring U is inserted between the link A and the door D, and urges the link A in the direction opposite to the arrow E in the figure, and the contact Ga prevents this rotation.
When the rigidity of the push spring U is zero, the link A is rotatably supported around the connection axis C, and the expansion / contraction part continues to move even when the door is stopped. The “switching means” involves no or little door rotation.
When the normal “switching means” operates without rotating the door, no load is applied to the operation of the closing device, and no load is applied to the spring. Since the spring expands and contracts in an instant, the “switching means” switches from “small” to “large” continuously and “accelerates the door” without requiring much time. In the case of FIG. 29, since the “switching means” involves a plurality of operations, “switching means”
Will take time.

When the rigidity of the push spring U is small, the “switching means” does the work of contracting the push spring U instead of rotating the door, and the loaded spring does not expand and contract instantly. In the process of shrinking the push spring U and accumulating “the force to rotate the door” in the push spring U, the movement of the telescopic part is transmitted to the door. There is no "rotating force". Wait while the latch is in contact with the door frame.
At the same time that the magnitude of the force accumulated in the push spring U reaches the “force for indenting the latch”, the door is sealed by the extension of the push spring U. At this time, the expansion / contraction part does not move and only the push spring U extends, and the force of the expansion / contraction part is not transmitted to the door. The force acting on the latch at the time of sealing is not excessive and insufficient, and the impact sound at the time of closing is minimized. When the door is sealed, the telescopic part moves again and strongly presses the door against the door.

When the rigidity of the push spring U is large, the link A is fixed to the door D, and the movement of the telescopic portion and the opening / closing movement of the door are linked. As shown in FIGS. 29B and 29C, a sliding surface KK is added to face the sliding surface K, and a path through which the wheel B can barely reciprocate between the sliding surface K and the sliding surface KK is provided. When provided, the movement of the expansion / contraction part is transmitted to the movement of the door, and at the same time, the movement of the door is transmitted to the movement of the expansion / contraction part. Since the movement of the telescopic part is transferred to the opening and closing movement of the door and the speed at which the door rotates is not the same as the speed at which the door rotates by inertia, the movement of the telescopic part and the rotational movement of the door will interfere with each other. . The movement in which the sliding surface K rotates the door and the movement in which the sliding surface KK prevents the door from being sealed interfere with each other. Further, in order for the door to close, it is necessary to exercise the above-mentioned “operation that shifts from a plurality of rods to movement”, and the door is not sealed until the plurality of operations are completed, and the door is not sealed.

If the change in the “force acting on the door” accompanying the rotation of the door is the same, the movement of the door is the same. When different forces are applied to the door in each rotation range of the door, it is better to use a spring with a different force and different rigidity in each rotation range than to control the force of one spring. It will be easy. 30 and 31 are plan views for explaining the operation of a rotating mechanism in which a spring working in the “(A) range” and a spring working in the “(A) range” are prepared separately and switched in the “switching range”. . 30 and 31 is a device relayed from a rotating device working in “range (A)” to a sealing device working in “range (ii)”.
FIGS. 30 and 31 consolidate the urging means of the rotating body J around the rotation axis Sw in order to reduce the size of the apparatus.
30 (a) to 30 (c), two springs having different rigidity act in series around the rotation axis Sw, and FIG.
0 (d) to (f) work in parallel. When the closed door is slightly opened, in FIGS. 30 (a) to 30 (c), the torsion spring UV1 having low rigidity expands and contracts, and in the rotation range of the separated separate doors,
Each spring with different stiffness is affected by the other. 30 (d) to (f) are not affected.

30 (a) to 30 (c), FIG. 30 (a) is in a fully open state, FIG. 30 (b) is a state diagram in the middle of closing,
FIG. 30C is a state diagram at the time of closing.
The rotating bodies J1 and J2 have the same rotating shaft and are rotatably supported around the fixed supporting shaft Sw. The torsion spring UV1 and the torsion spring UV2 are connected by a rotating body J1, and the torsion spring UV1 and the torsion spring UV are connected.
One of the two continuous bodies is attached to a spring support shaft S1 provided on the door frame W, and the other is attached to a spring support shaft S2 provided on the rotating body J2. Both the torsion spring UV1 and the torsion spring UV2 are U-shaped elastic bodies that are biased in the direction in which the support shafts at both ends approach each other. The rigidity of the torsion spring UV2 is large and the expansion and contraction is small.
FIG. 30 (c) shows a state in which the spring is most relaxed, and 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 drawing is prevented. The rotating body J2 comes into contact with the contact G2 where the door frame W is provided, and the rotating body J2 is prevented from rotating in the direction of arrow B in the figure.
When the rotating body J2 is rotated in the direction of arrow A in the figure as shown in FIG. 30B, the torsion spring UV1
The torsion spring UV2 is stretched together, and the torsion spring UV2 has a high 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”.
When the rotating body J1 comes into contact with G11 and further rotates in the direction of the arrow a in the figure, as shown in FIG. 30 (a), only the rotating body J2 rotates while the rotating body J1 is stopped, and the torsion spring UV1 expands and contracts. Only the torsion spring UV2 expands and contracts without doing so. In this way, different forces act on the doors in the “range of rotation of separate doors”.

FIGS. 30D to 30F are embodiments in which two different springs operate independently without being influenced by the other in the “divisional rotation range of separate doors”. 30
(D) is a state diagram at the time of closing, and shows a state where the spring has returned to its natural shape. FIG. 30E is a state diagram in the middle of closing, and FIG. 30F is a state diagram when fully opened. The rotating body J is rotatably supported around the fixed supporting shaft Sw, the springs U1 and U2 are elastic bodies formed in a U shape, one supporting shaft is the door frame W, and the other supporting shaft is the rotating body. Attach to J. In both cases, one of the support shafts is a fixed end and the other support shaft is a moving end, and a slider S is attached to each of the moving ends. The slider S moves along the groove H provided in the rotating body J or the door frame W, and swings between the start end Hs and the end He of the groove H.

The slider S1 of the spring U1 is accommodated in a groove H1 provided in the rotating body J, and the other end of the spring U1 is attached to a spring support shaft Sv1 provided in the door frame W. The slider S2 of the spring U2 is accommodated in a groove H2 provided in the door frame W, and the other end of the spring U2 is attached to a spring support shaft Sv2 provided in the rotating body J.
The slider S1 is in contact with the terminal end He1 of the groove H1 in the most loose state at the beginning of rotation shown in FIG. When the rotating body J rotates in either the direction of arrow A or B in the drawing, as shown in FIG. When the rotating body J further rotates, FIG.
As shown in (f), it moves away from the terminal end He1 along the groove H1 and reaches the starting end Hs1. The end He1 is at a position far from the fixed spindle 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 start 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 start end Hs1.

The slider S2 has the start end HS2 and the end H of the groove H2 with the spring shown in FIG.
In the middle part with E2, when the rotating body J rotates either in 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. The shape example of the groove | channel H2 in a figure is circular arc shape centering on the rotary body rotating shaft Q. FIG. 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 in contact with the start end Hs2 or the end end He2, the spring U2 changes from a state where the force for rotating the rotating body J does not work.
In the process of opening the door, force is stored in the spring U1 in the process of FIGS. 30D to 30E, and no force is stored in the spring U2. When the slider S2 comes into contact with the start end Hs2 or the end end He2 of the groove H2, if the slider S1 moves away from the start end He1 and comes into contact with the position of the fixed support shaft Sw, a force is stored only in the spring U2.

As shown in FIG. 30 (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. 30 (f), the door is opened, and the door is closed. This is a time when the state shown in FIG. 30 (f) where the force is stored shifts to the state shown in FIG. 30 (d) where the spring is loosened.
In the process of closing the door, when the spring U2 loosens from the state shown in FIG. 30 (f) and the slider S2 leaves the starting end Hs2 or the end He2 of the groove H2 as shown in FIG. 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 leaves the starting end Hs1 in the process of closing the door is smaller than the opening degree of the door when the slider S1 leaves the terminal end He2 in the opening process of the door. In this manner, the opening / closing device shown in FIGS. 30D to 30F biases the rotating body with different strengths of different sizes in the rotation range distinguished by the rotating body.

FIG. 31 shows “rotating means in the range (A)”, “rotating means in the range (I)”, and “switching means”.
In the same way as in the case of FIG. 30, the urging means that reciprocates linearly includes the case where only this urging means is attached to the door, and the case where other closing devices are attached to the door and the rotational force acting on the door. If they are the same, the door behaves the same. Therefore, the door provided with only this biasing means is the simplest and exhibits the same effect.
The passage body Sz is provided with a passage in which the action body A linearly reciprocates, and an end portion is attached to the fixed support shaft Sw. Operator
A is inserted into a through hole Hz provided in the passage body Sz, and is attached to the passage body Sz so as to be movable in the axial direction. FIG. 31 (a) shows a state in which the working body A is inserted most deeply into the passage body Sz.
1 (b) shows a state in which the action body A is most separated from the passage body Sz.
One end of the tension spring V1 is attached to a spring support shaft Vz provided in the passage body Sz, and the other end is attached to the working 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. As shown in FIG. 31 (b), the contact Ga attached to the head of the through bolt Va contacts the end of the through hole H in the “range (A)” and engages with the acting body A, thereby pulling the spring V1. Expands and contracts. As shown in FIG. 31 (a), when separated from the action body A by separating from the end of the through hole H in the “(range)”, the tension spring V1 does not expand and contract. The contact G of the through bolt Va engages or separates from the action body A, and the force of the tension spring V1 is transmitted to the action body A or is not transmitted.

A wheel B is mounted on the acting body A, and sliding surfaces K1 and K2 that move along the wheel B are provided on the sliding body KK. One end portion of the sliding body KK is rotatably supported around a connecting shaft P provided in the passage body Sz, and the other end portion is urged in a direction in which the wheel B is pressed by the pulling spring V2. As shown in FIG. 31 (a), when the wheel B moves along K2, the "force Fb that the wheel presses the sliding surface" moves the action body A in the direction of arrow A in the figure. As shown in FIG. 31 (b), when the wheel B moves along K1, "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. 31B shows the “rotating means in the range of (A)”. The contact Ga of the through bolt Va engages the acting body A, and the pulling spring V1 biases 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. 31 (a) shows “rotating means in the range of (i)”. 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 contact spring Ga of the through bolt Va moves away from the acting body A, and the tension spring V1 works ineffectively.

31 (c) and 31 (d) are provided with a passage body Sz, an action body A, and a free body AA in the middle, and the passage body Sz.
And a free spring AA, and a structure in which a push spring U1 is sandwiched between an acting body A and a free body AA,
31 (c) and 31 (d), the passage body Sz has a shaft SH1 at its center and SH2 on both sides, and the shafts SH1 and SH2 penetrate through a through hole HAA provided in the free body AA. The through-hole HAA of the free body AA moves along the shafts SH1 and SH2, and the through-hole HA of the action body A moves along the shaft SH2. It is. The loose body AA engages and separates from the contact G1 provided at the head of the shaft SH1, and the action body A engages and separates from the contact G2 provided at the head of the shaft SH2. Further, the contact Ga provided on the action body A is engaged with and separated from the free body AA. The rigidity of the push spring U1 is large, and the rigidity of the push spring U2 is small.

The process from FIG. 31 (d) to FIG. 31 (c) is a process of reducing the "distance between the fixed support shaft Sw and the connecting shaft C" by contracting the push spring U. U2 has little “increase in the force stored in the spring” even if the distance is greatly reduced, and the force stored in the push spring U2 slightly shrinks the highly rigid push spring U1, but as shown in FIG. If A and the free body AA come into contact and engage with each other through Ga and the distance does not decrease, the pressing spring U2 does not contract.
The process from FIG. 31C to FIG. 31D is a process in which the “distance between the fixed support shaft Sw and the connection shaft C” increases due to the restoring force of the pressing spring U, and the pressing with a large rigidity is performed. The spring U1 loses its force when the distance increases slightly. The push spring U2 having a small rigidity does not change the spring force even if the distance increases greatly. At the beginning of the increase of the distance from the state in which both of the pressing springs U1 and U2 shown in FIG. 31 (c) are contracted, both of the pressing springs U1 and U2 are extended at the same time. This is due to the pressing spring U1. The highly rigid push spring U1 is suitable for “(a) rotating means” in which the door rotates greatly with respect to a small movement of the drive unit and operates by the force of the large spring.
The push spring U1 loses force only by a slight increase in the distance, and thereafter the distance increases only by the expansion and contraction of the push spring U2. The push spring U2 having a small rigidity is suitable for “(i) rotating means” because the door rotates slightly with respect to a large movement of the drive unit and the force is not attenuated even by a small spring force. Thus, it is sufficient as a biasing means for the door by simply connecting the springs having different rigidity in series.

FIGS. 31 (e) and 31 (f) are provided with a passage body Sz, an action body A, and a free body AA between them, and a tension spring V1 between the passage body Sz and the free body AA, It is a structure that is connected by a pulling spring V2, and includes shafts SH1, SH2, through holes HAA, HA, and G1, G2 as in FIGS. 31 (c) and 31 (d). The rigidity of the tension spring V1 is small and the rigidity of the tension spring V2 is large. Per hit G
a and Gs are non-return devices that stop the movement of the free body AA in the direction of arrow A in the “switching range”.
Each of the hits Ga and Gs is rotatably supported by the passage body Sz and the action body A and is urged by the torsion spring UV, and rotation in the urging direction is prevented by the hit GG and the free body AA.
When the distance starts to increase from the state in which both the tension springs V1 and V2 shown in FIG. 31 (c) are contracted, both the tension springs V1 and V2 are simultaneously expanded. This is due to the tension spring V1 having low rigidity. The process from FIG. 31 (e) to FIG. 31 (f) is a process in which both the tension springs V1 and V2 are stretched to increase the “distance between the fixed support shaft Sw and the connection shaft C”. Initially, the tension spring V2 with high rigidity hardly expands and contracts, and the tension spring V1 with low rigidity expands and contracts so that the free body AA comes into contact with G1. When the free body AA hits and comes into contact with G1, the expansion and contraction of the tension spring V1 is blocked and only the tension spring V2 expands and contracts. The hits Ga and Gs rotate in the biasing direction of the torsion spring UV so that the free body AA does not return in the direction of arrow A in the figure.
The process from FIG. 31 (f) to FIG. 31 (e) is a process in which the tension spring V is contracted to decrease the “distance between the fixed support shaft Sw and the connection shaft C”. Only the tension spring V2 expands and contracts because it does not return in the direction of the middle arrow b. Ga and Gs come into contact with each other with the force that the tension spring V2 expands and contracts, the check device of the free body AA is released, and the large tension spring V2 hardly expands and contracts.
The tension spring V1 having a small rigidity expands and contracts.

The apparatus of FIG. 31 includes a rotation device that transmits rotation to the door only in “(A) rotation range”, and “(
(Ii) Rotation range ”only with a sealing device that transmits the rotation to the door, and with“ a biasing means that is valid halfway and becomes invalid from the middle ”and“ a biasing means that is halfway invalid and becomes valid from the middle ” The restraining means that works effectively in each rotation range is released in the “switching range”, and the force of the spring works invalid if the spring does not expand and contract, and the spring expands and contracts and works effectively.
As described above, if the biasing means of the opening / closing device of the present invention is an elastic body such as a pulling spring V, a pressing spring U, a torsion spring UV, a leaf spring, a molding spring, etc., the “force acting on the door” can be freely designed. I can do it.

When the door and the drive unit are not interlocked in the “switching range”, the movement of the “switching unit” is constant, and the time required until the “force acting on the door” becomes “the force that dents the latch male part Rd” Is constant. Further, the time required for the latch male part Rd to come into contact with the female part Rw and begin to dent is constant. If the door rotates only with the inertial force of the door, the amount of rotation of the door is proportional to the magnitude of the door inertial force, and the time required to switch from "(A) rotating means" to "(I) rotating means" The amount of rotation of the door during the period varies greatly depending on the magnitude of the door inertia force. FIG. 32 shows the “switching range”.
If the "(A) rotating means" simply switches the "(I) rotating means" and does not act on the door, the device that causes the door to stop suddenly by the amount that the door rotates only with the inertia force of the door works. It is operation | movement explanatory plan view of the switchgear which discriminate | determines whether it makes or not.

The device of FIG. 32 transmits the rotation to the door only in the “(A) rotation range” from the fully open state to just before closing, and the door only in the “(A) rotation range” from immediately before closing to the fully closed state. It is equipped with a sealing device that transmits rotation. The “link A1 for mounting the wheel B1” is pivotally supported around the “connection shaft C provided on the door D”, and is urged by the torsion spring UV1 in the direction of the arrow A in the figure. The rotating body J is rotatably supported around the fixed support shaft Sw, and is urged by the torsion spring UV2 in the direction indicated by the arrow C in the figure. A link A2 is connected to the connecting shaft P provided at the tip. The wheel B2 is attached to the tip of the link A2.
As shown in FIG. 32 (a), in the “range (A)”, the wheel B1 moves along the sliding surface K1 in the direction indicated by the arrow D in FIG. It rotates in the direction of arrow B in the figure. Before the closing, the rotation of the link A1 in the direction of the arrow a in the drawing is prevented by Ga, and at the same time, the door is not rotated by the wheel B1, and the door is rotated only by dynamic inertia.
The wheel B2 is pushed out by the wheel B1 as shown in FIG.
As shown in (b), it moves on the sliding surface K2. At this time, the wheel B1 does not contact the sliding surface K11 and the door can be freely closed and rotated.

A rotating body J, a link A2, and a wheel B2 indicated by a solid line in FIG.
The link A can move with a weak force perpendicular to the direction of the axis line Za of the link A while supporting a strong pressing force in the direction of the axis line Za. When the stationary state is maintained by the toggle spring VV shown in FIGS. 12D to 12F, the stronger the toggle spring VV, the more difficult the link A2 rotates.
In order to release the stationary state, “(a) rotating means” needs to be powerful. Therefore, the toggle spring VV is located at a position close to the link “A2 center of rotation Sw2” of the toggle spring VV.
Since the shaft core line slightly moves so as to cross the “rotation center Sw2 of the link A2”, the standby state is kept very unstable. On the other hand, when the “rotating mechanism in which the wheel B2 presses the sliding surface K2” is adopted as shown in FIG. 32A, the angle Θak is sufficiently obtuse as shown by the solid line in FIG. Even if it exists, the standby state is canceled by a small force acting in the circumferential direction of the circular motion of the wheel B2, and the standby state becomes very stable.

A solid line shown in FIG. 32A shows a state in which a pressing force is applied along the axial center line of the link A2 by the rotational force of the rotating body J in the direction indicated by the arrow C in FIG. The crossing angle Θa2 between the axial center line Za2 of the link A2 and the sliding surface K11 is an obtuse angle, and the rotation of the link A2 in the direction indicated by arrow E in the drawing is prevented by Gj1.
In FIG. 32A, the axial center line Zj of the rotating body J, the axial center line Za of the link A, and the wheel B2 indicated by broken lines are pushed out of the sliding surface K11 by the movement of the wheel B1 in the direction indicated by the arrow D in the figure. Indicates the state. A step is provided between the sliding surfaces K11 and K2, and when the rotation axis of the wheel B2 passes the step, half of the wheel diameter moves by itself while dropping the step. The intersection angle Θa2 turns to an acute angle, and the wheel B2 tends to move in the direction of the arrow in the drawing along the sliding surface K2.
The sliding surface K2 is rotatably supported around a connecting shaft Cj provided on the door D and is urged by a push spring U3 in the direction indicated by an arrow H in the figure, and rotation in the direction indicated by the arrow H is prevented by Gk2. . As the wheel B2 moves along the sliding surface K2 in the direction of the arrow in the drawing, the sliding surface K2 rotates around the connection axis Cj in the opposite direction to the arrow H in the drawing, and the gradient of the sliding surface K2 is The wheel B2 becomes smaller and can move on the sliding surface K2 toward the terminal end Ke2. Wheel B2 is sliding surface K
2 is initially before the wheel B2 gets over the connecting shaft Cj, and the “push spring U attached around the connecting shaft Cj” is urged in the direction to open the door D as in the case of FIG. To do. When the wheel B2 is on the rotation axis Cj of the sliding surface K2, the base end Ko2 is separated from the door frame W, and all the pressing force of the wheel B2 presses the door D. The wheel B2 moves toward the terminal end Ke2, and the “action line Fb of the force with which the wheel B2 presses the sliding surface K2” moves away from the pivot axis O.

The force that the rotating device acts on the door is the force that the wheel B1 presses the sliding surface K1 by the torsion spring UV1, and the force that the sealing device acts on the door is that the wheel B2 slides on the sliding surface K2 by the torsion spring UV2. It is the force which presses. The rotating device and the sealing device each have their own force, and the magnitude of each force can be freely adjusted by changing the strength of the torsion springs UV1 and UV2 regardless of the position of the action point. Also, since the rotating device operates separately in the “(A) range” and the sealing device operates separately in the “(A) range”, the force acting on the door in the “(A) range” and the “(A) range”. "
Thus, the force acting on the door can be freely adjusted by changing the magnitude of the force of the torsion springs UV 1 and UV 2 regardless of the position of the action point. Depending on the magnitude of the force of the torsion springs UV1 and UV2, "(A)
It is conceivable that the position of the force applied to the door in the “range” is farther from the pivot O than the position of the point of action of the force acting on the door in the “(range)”.
FIG. 32 (c) shows a state when the wheel B2 returns to the sliding surface K11 in the process of opening the door. In the process of opening the door, “the opening degree of the door when the wheel B2 reaching the terminal end Ke starts to return” is shown. “Θdo” indicates that it is larger than “the opening Θds of the door when the wheel B2 is transferred onto the sliding surface K2” in the process of closing the door. The door that starts to close from the opening Θdo of the door has an inertial force until the opening of the door reaches Θds, and the wheel B1 can push the wheel B2 from the sliding surface K11. In the door that starts to close from the door opening smaller than Θdo, wheel B2 is sliding surface K
2 and within the range where the sealing device operates, the door is sealed.

32 is a device that relays from the rotating device to the sealing device immediately before closing, and when relaying from the rotating device to the sealing device, it works to move the stationary sealing device, so that the door is decelerated.
Since the sealing device starts without rotating the door, the distance that the door moves with dynamic inertia while relaying from the rotating device to the sealing device is proportional to the rotational speed of the door. large.
“While relaying from the rotating device to the sealing device” means that a part of the wheel B1 moves the wheel B2 on the sliding surface K11.
After part of the wheel B1 pushes out the wheel B2 from the sliding surface K11 until the wheel B2 gets over the connecting shaft Cj after being pushed out from above, the wheel B1 does not rotate the door.
Further, the wheel B2 does not rotate the door until the wheel B2 falls on the step and moves onto the sliding surface K2 and over the connecting shaft Cj.

A link A3 is attached to the end of the sliding surface K2, and a wheel B3 is attached to the tip of the link A3.
As shown in FIG. 32 (d), when the tip K2o of the sliding surface K2 comes into contact with the door frame W just before sealing, the link A3 is in an upright state. The sliding surface K3 is rotatably supported around a support shaft Sk3 provided on the door frame W, and is urged by a pressing spring U3 in the opposite direction to the arrow G in the drawing, and the rotation in the direction opposite to the arrow G in the drawing hits Gk3. Is blocked by.
When the door rotates at a low speed, the amount of rotation of the door is small “while relaying from the rotating device to the sealing device”, the wheel B3 abuts on the sliding surface K3, and the sliding surface K3 rotates in the direction indicated by the arrow in the figure. The amount is small, the intersection angle Θa3 of the axis A3 of the link A3 and the sliding surface K3 is an acute angle, and the wheel B3 can move in the direction of the arrow in the figure. As shown in FIG. 32 (b), when the wheel B2 moves on the sliding surface K2 and gets over the connecting shaft Cj, the link A3 falls.
When the door rotates at a high speed, the amount of rotation of the door is large “while relaying from the rotating device to the sealing device”, the wheel B3 contacts the sliding surface K3, and the sliding surface K3 rotates in the direction indicated by the arrow in the figure. The crossing angle Θa3 between the axial center line Za3 of the link A3 and the sliding surface K3 is an obtuse angle, and the movement of the wheel B3 in the direction indicated by the arrow in FIG. As shown in FIG. 32 (d), the wheel B3 does not move on the sliding surface K3, and the link A3 remains upright. The wheel B2 cannot move on the sliding surface K2 in the direction of the arrow in the figure, and the door is stopped and the sealing is prevented.

FIG. 33 is a plan view for explaining the operation of the latch. The spring force required to rotate the door is small, and a large sealing force acts on 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. If a magnetic catch is installed instead of a latch, the force of the spring to seal the door is not necessary, and it will be felt lightest when the door is opened.
Thus, if the resistance of the latch is small at the time of sealing, the door can be rotated with a force slightly exceeding the static maximum frictional force until it sufficiently hits the door. In other words, the object of the present invention of “slowly closing and always sealing” is made more possible. FIG. 33 provides a latch that has a low resistance when the door is closed and prevents the door from reversing, and reduces the force when opening the closed door by reducing the sealing force. The force of the spring that presses the door at the time of sealing is set to a force that keeps the door airtight, and it is not stronger than that.

FIG. 33 is a horizontal sectional 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. FIGS. 33 (a), (b), and (c) show the states when closing, immediately before closing, and when opening.
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. Circumference Rf
The shape of is centered on “the position of the rotation support shaft Ig0 of the claw Ge when closed”, and “the rotation support shaft Ig and the claw G
It is a part of a circle having a radius “the distance rr between the tip end portion Pg of e”.

FIG. 33A 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. The line of action of “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 Pg of the claw Ge, and “force Fg for preventing reverse rotation” is the rotation support shaft Ig. Supported. For this reason, it is necessary to increase the cross-sectional area of the rotation support shaft Ig.
In the latch device shown in FIG. 4, a circumferential portion Re is provided in the recess He that accommodates the claw Ge, and most of the “force Fg for preventing reverse rotation” is not on the rotation support shaft Ig but on the circumferential portion Re. Supported by range.
A peripheral portion on the opposite side of the tip portion Pg of the claw Ge is provided with a circumferential portion Rg, and the circumferential portion Rg is a rotation support shaft Ig.
Is a part of a circle having a radius r, and a circumferential part Re of the recess He is a part of a circle having a radius greater than or equal to 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 push spring U is attached to the concave portion He of the latch male part E, and urges the claw Ge about the rotation support shaft Ig in the direction of arrow A in the figure. As shown in FIG. 33 (c), the tip portion Pg of the claw Ge protrudes from the recess He in a state away from the door frame W. In addition, the tip R of the range Re of the circumference Re
ee and its periphery serve as a hit to prevent 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 protrusion.
As shown in FIG. 33 (c), when the door D moves from the state separated from the door frame W to the state immediately before closing shown in FIG. Surface Ke is the entrance Kf
The claw Ge rotates around the rotation support shaft Ig in the direction of the arrow B in the figure and is accommodated in the recess He provided in the latch male part E, and the claw Ge is accommodated inside the door. When the door D further rotates, the claw tip Pg moves on the circumferential portion Rf of the recess Hf after passing over the inlet portion Kf of the latch female portion F as shown in FIG.
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, D is door-to-door Gw
When the door is about to move in the direction indicated by the arrow D in FIG. Even when Ge does not enter the recess Hf of the latch female portion F deeply, the door does not move in the direction of the arrow D.

In a normal latch device, when the latch abuts on the door frame W, the latch moves parallel to the door surface, and a force acts in a direction perpendicular to the moving direction. The force that prevents the door from reversing is a shearing force, and the supporting portion is supported by a large contact portion on the side surface of the latch. A large force is required by changing the direction of the force acting on the latch to a right angle and the frictional resistance acting on the side surface of the latch.
On the other hand, the latch device of the present invention makes the moving direction of the latch and the direction of the force acting on the latch close to each other by rotating the latch. In this way, the force for denting the latch is reduced, and the sealing force acting on the closed door can be reduced. In the latch, the force is directed toward the rotation axis, and the portion that supports this is supported by the outer edge of the latch, not the rotation axis of the latch, and is supported by the large contact portion. Even if the door frame does not enter deeply, it does not come out of the door frame, and the greater the force that opens the door, the greater the braking force.

33 (d) to 33 (f) are obtained by replacing the claw Ge of FIGS. 33 (a) to (c) with “claw Gb whose outer edge portion is a spiral curve”, and the outer edge is the outer edge from the rotation axis Ig. It is a spiral curve in which the distance to becomes gradually larger. As shown in FIG. 33 (a), “a contact point b between the claw Gb and the latch female portion F”.
The distance Lb between the rotation axis Ig and the rotation axis Ig increases as the claw Gb rotates in the direction opposite to the arrow B in the figure. Therefore, when the door is opened from the state shown in FIG. The "force acting in the direction of expanding Lg" increases, and resistance is applied around the pivot axis O to prevent it from opening.
When the door is closed, the claw Gb rotates in the direction indicated by the arrow B in the figure, and “a contact b between the claw Gb and the latch female portion F is obtained.
”And the rotational axis Ig becomes small, and the door can be brought into contact with the door without any substantial resistance. In the latch device shown in FIGS. 33 (d) to 33 (f), the latch female part F shown in FIGS.
33 (a) to 33 (c) and the claw Gb of FIGS. 33 (d) to 33 (f) have a large sealing force in the radial direction as in the “sealing mechanism in which the wheel B presses the sliding surface K”. Is a latch that rotates with a small circumferential force and has a low resistance when the door is closed, and a large resistance in the opening direction.

The “switching means” of the present invention is such that the line of force acting on the “support shaft provided at the tip of the rotating body that rotates about the rotating shaft” crosses the rotating shaft at the “predetermined opening of the rotating body”. When the urging direction of the rotator is reversed, and a releasable restraining means for preventing the rotation of one of the rotators is provided, such as a rotation mechanism in the door closing process, When the size is switched and the restraining means is not provided, the urging direction is reversed as when the door is stationary at the fully open position.
FIG. 34 is a “switching means” that does not include a restraining means. When the door that is stationary in the fully open position is slightly rotated in the closing direction, the biasing direction is reversed and the door is closed to the fully closed position without permission. However, the “switching means” is provided so that the urging direction reverses and opens to the fully open position without permission, and a door is provided that opens fully when it is slightly opened and fully closes when it is slightly closed.

One of the tension springs V is attached to a support shaft Sd provided at the door, and the other is attached to a support shaft Sa provided at the tip of the link A, and the door is pulled to rotate. When the link A is urged by the toggle spring VV and swings between the positions of contact with the fixed support shaft Sw and contact with Ga1 and contact with Ga2, and the contact with the contact Ga1 as shown in FIG. It rotates in the direction of arrow A in the figure around the pivot axis O, and fully contacts with the door stop Gd1. When contacting the contact Ga2, as shown in FIG. 34 (d), the door D rotates in the direction opposite to the arrow A in the figure and contacts the door contact Gd2 and is fully closed.
Rotating bodies J1 and J2 are means for abutting and separating from the wheel B mounted on the link A to swing the link A, and are rotatable around fixed support shafts Sw1 and Sw2 provided on the door frame W, respectively. Pivoted,
The torsion springs UVj1 and UVj2 are energized in the direction indicated by the arrow C in the figure and are in contact with Gj1 and Gj2 and stand by. Further, the sliding surfaces KK1 and KK2 are provided in the radial direction and the vortex line in the circumferential direction, and the sliding surfaces KKK1 and KKK2 are provided in the radial direction opposite to the sliding surfaces KK1 and KK2. Wheel B has sliding surfaces KK1 and KK as shown in FIG.
2 and reciprocates between the standby positions of the rotating bodies J1 and J2.

The sliding surfaces K1 and K2 are vortex lines that gradually move away from the rotation shafts Sw1 and Sw2 from the base end portions Ko1 and Ko2 to the terminal ends Ke1 and Ke2, respectively. The end portions Ke1 and Ke2 are engaged with the surfaces KKK1 and KKK2 and retracted in the direction opposite to the arrow B in the figure, and moved forward in the direction of the arrow B in the figure while retracting from the sliding surfaces K1 and K2. The ratchet claws AA1, AA2 are respectively supported by the support shafts S1,
Gaa1, Gaa2 supported by torsion springs UVaa1, UVaa2 and pivoted around S2
Waiting for contact. As shown in FIG. 34 (a), when fully closed, the ratchet pawl AA1 is engaged with the sliding surface KKK1, and the wheel B is in contact with the sliding surface KK1. As shown in FIG. 34 (d), the ratchet pawl AA2 engages with the sliding surface KKK2 and the wheel B contacts the sliding surface KK2 when fully opened.

When the door that is stationary at the fully closed position is slightly opened as shown in FIG. 34 (b), the ratchet claw AA1 engaged with the sliding surface KKK1 shows the rotating body J1. Rotate in the opposite direction to the middle arrow C, the sliding surface KK1 presses the wheel B, and the link A rotates in the direction of the arrow D in the figure.
As shown by the broken line, when the axial center line Zv of the tension spring V and the axial center line Za of the link A pass, the link A is rotated to a position where it abuts against Ga2 by the toggle spring VV and stops. The urging direction of the tension spring V is reversed from the closing direction to the opening direction and opens to the fully open position without permission. One of the toggle springs VV is attached to the link A, while the other is attached to the door frame W on the “straight line T passing through the pivot axis O and the fixed support shaft Sw”.
The end portion Ke2 of the sliding surface K1 approaches the pivot axis O as the rotating body J1 rotates in the opposite direction to the arrow C in the figure, and the rotation of the arrow c in the figure of the ratchet pawl AA1 is prevented by Gaa1 Therefore, after the link A comes into contact with the contact Ga2, the ratchet pawl AA1 moves away from the sliding surface KKK1, and the rotating body J1 is returned by the torsion spring UVj1 as shown in FIG. 34 (c), and the contact Gj1, Gj2
Wait for contact.

FIG. 34 (c) shows a state in which the ratchet claw AA2 moves along the sliding surface K2, and the ratchet claw
AA2 hits against the biasing force of the torsion spring UVj2 in the direction of arrow C in the figure, moves away from Gaa2, and advances in the direction of arrow B in the figure while retracting from the sliding surface K2.
FIG. 34 (d) shows a state in which the ratchet claw AA2 has passed over the end portion Ke2, and the ratchet claw AA2
Is rotated in the direction opposite to the arrow C in the figure by the torsion spring UVj2, and after contacting with Gaa2, is engaged with the sliding surface KKK2 of the rotating body J2.
The process of returning from the fully open position to the fully closed position follows the reverse of the above-described process. When the door stationary at the fully open position is slightly rotated in the closing direction, the urging direction is reversed and the door is closed to the fully closed position without permission.
In the switchgear of FIG. 34, the rotation axis of the link A is far from the pivot axis O and the swinging width is reduced.
The ratchet pawl is located far from the pivot axis O and has a large moving distance with respect to the rotation angle of the door so that the urging direction of the door is reversed only by slightly rotating the door at the fully open position or the fully closed position. ing.

FIG. 35 illustrates that “the wheel B attached to the tip end portion of the link A moves on the sliding surface K” and “the crossing angle Θak between the sliding surface K and the axis A of the link A” moves to the obtuse angle side. FIG. 35 (a) to (c) are operation explanatory views employed in shoes, and FIG. ), (c) are explanatory views of the operation adopted for the foot pedal.
The shoe shown in FIG. 35 has no resistance when the forefoot lands, and the force that kicks the ground when the rear foot leaves the ground maximizes the energy with which the rear foot kicks the ground when the foot lands. There is a feature to store. In the biped walking, the moment when the hind legs are separated from the ground and stand only with the front legs is balanced by the motion acceleration in a state where the forces are not balanced mechanically. Therefore, the greatest force is required when the rear foot kicks the ground. In the case of a push spring, the force is minimized by the hind legs extending away from the ground.
The shoe shown in FIG. 35 is divided into a shoe D and a shoe sole W in two parts, and is connected by a pivot O. FIG.
FIG. 35B shows a state where the shoe has landed, FIG. 35B shows a state where the shoe is about to leave the ground, and FIG. 35C 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.

The process from FIG. 35 (a) to FIG. 35 (c) is the process from the landing of the shoe to the kicking up of the foot. 1 is difficult to stand still, but in the shoe employing the spring rotation mechanism of FIG. 1, the spring force hardly acts on the shoe at the time of landing, as shown in FIG. As shown in the figure, even if the shoe rotates and the shoe sole opens slightly, the “distance between the force acting line Fb and the pivot O” does not change. 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 FIG. 35 (c), when the shoe leaves the ground, a large force Fb acts on the shoe sole and kicks the ground.
The spring rotation mechanism shown in the embodiment of FIG. 35 is the spring rotation mechanism shown in FIG. 1 in which the magnitude of the force is switched at a predetermined opening degree of the shoe at the moment when the shoe leaves the ground. It is added to the robot's feet.
The process from FIG. 35 (a) to FIG. 35 (c) is “the angle Θak on the moving direction side of the wheel B (in the direction of arrow E in the figure) at the angle between the sliding surface K and the axial center line Za of the link A”. Is an acute angle, resists movement of the wheel B, and works to open the two opening / closing bodies D and W on the pivot O-axis. FIG. 35 (c) to FIG.
In the process up to 5 (a), in the process until the shoes in the air land, the moving direction of the wheel B is reversed (the direction opposite to the arrow e in the figure), and “the angle Θak on the moving direction side of the wheel B” Becomes an obtuse angle, and resistance to the movement of the wheel B is not applied. “Shoes with springs simply attached to the sole” receive a sense of resistance as they land, but when walking with the shoes shown in FIG. 35, walking and leaving the ground are both normal walking and sensory. There is no place to change and there is no sense of incongruity even though the spring operates.

FIGS. 35 (d) and 35 (e) are explanatory views of the operation of the foot pedal adopting the spring rotation mechanism shown in the embodiment of FIG. 1. In order to surely return to the original position, it is necessary to increase the force of the spring. There is a spring with strong restoring force. 35 (d) and (e), like the shoes of FIGS. 35 (a) to 35 (c), have a feature that the force when stepping on is small, and it is difficult to get tired even if it is stepped on many times.
The foot pedal D is rotatably supported around a pivot O provided on the vehicle body W, and a link A is connected to a connection shaft C provided at the tip. The link A is urged around the connection axis C by a pushing spring U in the direction of arrow A in the figure, and the rotation of the link A in the same direction is prevented by the contact Ga. Link A
A wheel B is mounted on a rotation axis Ib of a wheel provided at the tip of the wheel B, and the wheel B moves along the sliding surface K. FIG. 35D is a state diagram in which the foot is separated from the foot pedal D, and FIG. 35E is a state diagram in which the foot pedal D is separated by the foot.

In the process from FIG. 35 (d) to FIG. 35 (e), when the foot pedal D is stepped on with the foot and rotated in the direction opposite to the arrow B in the figure with the pivot O as the axis, the push spring U contracts and the link A is connected. The wheel B rotates about the axis C in the direction opposite to the arrow A in the figure, and the wheel B moves along the sliding surface K in the direction of the arrow E in the figure. As the link A rotates in the direction opposite to the arrow A in the drawing, the acting force distance Lo increases, and the pressing force Fb that balances the driving force Mv acting around the connecting shaft C decreases, and “stepping on the foot pedal D with your foot” "Force" becomes small. Further, “the angle Θak on the moving direction side of the wheel B at the intersection angle between the axial center line Za of the link A and the sliding surface K” is an obtuse angle, and no resistance is applied to the movement of the wheel B.
In the process from FIG. 35D to FIG. 35E, the foot pedal D is released from the foot pedal D.
FIG. 35 (e) shows a state where the foot pedal is fully depressed.
Although the acting force distance Lo is maximized, the pushing spring U is maximally contracted, and the acting line of the pushing force Fb is substantially perpendicular to the sliding surface K. In order to return to the position of FIG. 35 (d), the force of the spring is the maximum, the direction of the force is the most effective, and the “angle Θak on the moving direction side of the wheel B” is an acute angle. Just as resistance is applied, power is transmitted to the foot pedal.

Even in the case of an accelerator pedal of an automobile, it is preferable that the initial speed when the foot pedal starts moving in the return direction at the moment when the foot is released from the foot pedal, and when the sliding surface K is flat, The force acting on the foot pedal at the moment of releasing is maximum.
Also in the “rotating mechanism in which the wheel B attached to the tip of the link A rotating about the connecting shaft C presses the sliding surface K” in FIG. 1, “rotating body J and link A shown in FIGS. In the “rotating mechanism connected to each other by the connecting shaft P”, when the “axial axis Za of the link A passing through the connecting shaft C or the connecting shaft P and the force acting line Fb” are close to each other, the axial core Za of the link A Even if a large force is applied in the direction, it moves with a small force in the perpendicular direction, but on the contrary, “the axial line Za of the link A passing through the connecting axis C or the connecting axis P and the force acting line Fb” and the field. When the angle is large, even if a large force is applied in the direction perpendicular to the axis A of the link A, it moves with a small force in the direction of the axis Z. In the case of the door of FIG. 4, the “rotating mechanism in which the wheel B attached to the tip of the link A rotating about the connecting shaft C presses the sliding surface K” is a strong spring in “range (A)”. In the case of the foot pedal shown in FIG. 35, the “force acting on the pedal” is small while using a strong spring force so as to surely return so that the “force acting on the door” is small while using the force.
The state of FIG. 35 (e) corresponds to the “range (A)” shown in FIG. 1 (a) and is a state in which the wheel B is held and restrained in the vicinity of the pivot axis O. The process leading to d) is a “switching range” in which the foot pedal D is slightly rotated to return to a position far from the pivot axis O with a slight rotation. The embodiment shown in FIGS. 35D and 35E uses only the “switching range” of the rotating mechanism shown in FIG.

When the link A stands up to a right angle with respect to the sliding surface K, the force that the foot pedal D returns to the state shown in FIG. 35 (d) becomes strong, and a large force is required to step on the foot pedal D. When the moving surface K is a plane, the rotation of the link A in the direction of arrow A in FIG. 35 must be stopped by Ga before the angle Θak becomes a right angle as shown in FIG. When the sliding surface K is a flat surface, the resistance applied to the stepping foot is large at the beginning of the step and then gradually decreases. However, the shape of the sliding surface K is as shown by the broken surface in FIG. If the concave surface is formed such that the distance between the “contact point b between the wheel B and the sliding surface K” and the connecting shaft C is gradually increased, the resistance at the beginning of the step can be reduced.
The sliding surface KK indicated by a broken line in FIG. 35 (d) is similar to the sliding surface K shown in FIG. 4 and “the line of action of the force Fb that the wheel B presses the sliding surface K” and the center of rotation of the link A. The distance Lo between
The sliding surface K shown in Fig. 4 makes the pedaling force as uniform as possible from the beginning to the end.
In FIG. 35, the link A supports a large force while keeping the acting force distance Lo small.
A sliding surface KK indicated by a broken line in d) keeps the acting force distance Lo large, so that the wheel B can easily move even if the axial force of the link A is small.

FIG. 36 is the same as described in FIG. 8 because “the rotation axis C of the link A crosses the axial center line Zv of the spring”.
It is an embodiment that utilizes the rotation mechanism that starts the switching means in industrial fields other than doors,
36 (a) to 36 (c) are operation explanatory views of the robot arm using the feature that the “switching means” does not involve any rotation of the opening / closing body of the opening / closing body, and FIGS. It is operation | movement explanatory drawing of the closing machine using the characteristic that a means starts at the predetermined opening degree of an opening-closing body.
If FIG. 35 is a leg of a robot arm, FIGS. 36 (a) to 36 (c) are fingers of the robot arm, FIGS. 36 (a) to 36 (c) are arms D and W shown in FIG. , Share Axis O 1
In this embodiment, the arms D are connected by a tension spring V, and the arm D rotates in the direction of the arrow B in the figure by the expansion and contraction of the tension spring V. is there.
FIG. 36 (a) shows the moment when the egg Egg is gripped by the tips of the two arms D and W. FIG. In the device for grasping with a normal object sandwiched, the gripping force increases and at the same time the two arms D and W rotate in the closing direction and the eggs are crushed, but the process of FIGS. 36 (a) to 36 (b). As shown, the link device continues to move even when the rotation of the two arms D and W is stopped. As shown in FIG. 36 (b), the link A rotates about the connection axis C in the direction of the arrow A in the figure to move the spring axis Zv away from the pivot O and increase the force to grip the egg Egg. Thus, the state in which the opening degree Θd of the arm D and the gap Le are not changed is maintained, and only “the force Fe to grip the egg” can be increased without crushing the egg.

One support shaft Sw of the spring is provided on the arm W, and the other support shaft Sa is provided on the tip of the swing link A.
The swing link A is rotatably supported around a rotation support shaft C provided on the arm W, and the swing link A is rotated around the rotation support shaft C by “Ga1, Ga2 per engagement / disengagement with the swing link A”. On both sides.
FIG. 36 (a) shows that the connecting shaft is engaged with the swing link A and the contact Ga1 in the “range (A)” while keeping the “distance Lo between the rotating shaft O and the spring axis Zv” small. C is a state diagram in which C moves on the circular orbit R0 in the direction indicated by the arrow B in the drawing to cross the axial center line Zv of the pulling spring V, and the distance Lo is small and the force Fe pressing the egg Egg is small.
FIG. 36 (b) is a state diagram in which the connecting shaft C crosses the spring axis Zv, the urging direction of the pulling spring V changes, and the link A rotates in the direction indicated by the arrow A in FIG. It swings from the pressing position to the position where Ga2 is pressed, the distance Lo increases, and the force Fe pressing the egg Egg also increases.
The rotation of the link A in the direction of arrow A in the drawing is not related to the door at all and is executed even when the door is stopped.
By providing one support shaft Sw of the spring close to the rotation support shaft C of the swing link A and the other support shaft Sa far, the swing link A moves around the rotation support shaft C in the direction of the arrow a in the figure. When rotating, the distance between the action line Zv of the spring force and the rotation support shaft C is kept small, the expansion and contraction of the spring accompanying the rotation of the swing link A is small, and the acceleration of the swing link A is small. . The factor that accelerates the swing link A is not the strength of the spring but the amount of expansion and contraction of the spring, and “the difference between the spring force at the start and end of the movement”
It is.

A push spring U is attached to the tip Dw of the robot arm W. The push spring U has the same function as the push spring U of FIG. 1, and the connection axis C is the axial center line Zv of the tension spring V as shown in FIG.
When the rotation of the arm D stops before crossing the link A, even if the link A remains in contact with the contact Gj, the push spring U can be contracted with a small force "(A) rotating means" and the door By rotating, the connecting shaft C crosses the axial center line Zv of the spring.
A broken line Das in FIG. 36A shows the arm D when the egg Egg is small, and the “switching means” starts to operate when the connecting shaft C crosses the axis A of the link A before the push spring U contracts. It is faster than the case indicated by the solid line. The “switching means” operates while the push spring U is contracted regardless of whether the press spring U is before or after contraction, and “the egg Esg indicated by a broken line” increases as the acting force distance Lo increases.
The force Fe ”for grasping is increased, but the force Fe for grasping the egg Egg is proportional to the contraction of the push spring U. When the rigidity of the push spring U is small, most of the decrease in the distance Le is contraction of the push spring U, and the egg Eg
There is little shrinkage of g. In the process of FIG. 36 (a) to contact b), only the “force to grip the egg Egg” increases without deforming the egg.
The broken line in FIG. 36 (b) shows the arm D when the egg Egg is small, and the amount of expansion / contraction of the tension spring V is smaller than that indicated by the solid line. Accordingly, the pressing spring U is less contracted, and the “force Fe for gripping the egg Es indicated by the broken line” is also reduced. If it ’s small and there ’s no big difference in egg size,
The force “Fe to grab Egg” is finally fixed.

The “(range)” including the “switching range” is narrow, and the link device moves greatly against a slight rotation of the door just before the door closes. When opening a closed door, it is highly resistant to rotate the link device greatly in the opposite direction by opening the door slightly and return it from “(i) rotating means” to “(a) rotating means”. It will be.
In FIG. 1, the opening when the wheel B far from the pivot O is returned to the vicinity of the pivot O when the door is opened is determined based on the opening degree of the door when the wheel B which is in the vicinity of the pivot O immediately before closing starts moving. The degree is great. FIG. 36 (c) shows the door when the link A is in contact with Gj2 in the process of opening the arm D and the connection shaft C again crosses the spring axis Zv and returns to contact with Gj1. The opening degree Θdo is larger than Θds shown in FIG. Thus, the great force of the “(i) rotating means” is facilitated by the large door rotation when the door is opened.

36 (d) and 36 (e) are explanatory views of the operation of the closing machine in which the string St always binds the item box with a constant force. The “switching means” starts at a predetermined opening, but if the opening degree at which the “switching means” starts is proportional to the magnitude of the force, the “switching means” starts when the predetermined force is reached. It becomes like this.
36A to 36C, if the size of the egg Egg is constant, the predetermined opening degree at which the “switching means” starts is determined by the amount of contraction of the push spring U. 36 (d) and (e) are the same as FIG.
The rotation mechanism is the same as that of 6 (a) to 6 (c), and the “switching means” is started when the distance Le is a predetermined size. The predetermined size of the distance Le is also determined by the amount of compression of the pressing spring U, and the amount of compression of the pressing spring U is the product box.
Therefore, the “switching means” is started when the tension acting on the string St that binds the item box reaches a predetermined force. The structure of FIGS. 36A to 36C is shown in FIGS.
Corresponding to the structure shown in d), the structures shown in FIGS. 36D and 36E correspond to the structures shown in FIGS. 8E to 8F.

As shown in FIG. 36 (d), one end of the string St is fixed to a take-up roller Rol that is attached to the arm D, passes between the two arm tip portions Da and Wa, and surrounds the periphery of the product box. The item box is bound through the two arm tips Da and Wa. The arm distal end Wa is “the distal end of the rotating body J that is rotatably supported around the support shaft Sj provided on the arm W, and the support shaft Sw of the tension spring V is provided at the base end.
By pulling the other side of the string St, the string St presses the arm tip Wa and contracts the push spring U to rotate the rotating body J in the direction indicated by the arrow C in the figure. At the same time, the support shaft Sw of the pull spring V becomes the support shaft Sj. The shaft axis line Zv of the spring crosses the connecting axis C by revolving around.
FIG. 36 (e) shows a state in which the wheel B moves in the direction of arrow A in the figure and the arm D rotates in the direction of arrow B in the figure, and the two arm tip portions Da and Wa are closed. A portion DW having a crimping function and a portion WD having a cutting function are attached to the arm tip portions Da and Wa, and two arm tip portions Da,
At the same time that Wa is closed, the string St is crimped and cut.

The rotation mechanism of the present invention has a "(A) range" in which the operation of the drive unit is small and the door rotates greatly.
In the “range”), the drive part is operated with a small amount of rotation of the door. Therefore, in the “switching range” of the rotation mechanism of the present invention, the door is almost interlocked with the drive part slightly interlocked. When a damper is attached to the drive part of the switching means that does not involve rotation, the damper works invalidly in the “(A) range” and works effectively in the “(A) range” to buffer the collision that occurs at the end of the rotation. , Does not resist the previous rotation.
FIG. 37 attaches a damper to the door drive unit shown in FIG. 27 so that the “switching means” does not end the operation in an instant when there is no load. Therefore, if the spring for rotating the door is removed from the opening / closing device shown in FIG.

FIG. 37 has the same structure as FIG. 27, and removes the spring urging around the connecting shaft PP in FIG. 27 so that the connecting shaft PP does not cross the “straight line passing through the connecting shaft C and the fixed support shaft Sw”. ing.
FIG. 37A is an operation explanatory diagram of “range (A)”, and the process from FIG. 37 (a) to contact b) is an operation explanatory diagram of “switching range”. In the “switching range”, the door rotates slightly and the rotating body J rotates significantly. As means for slowing the operation of the rotating body J, as shown in FIG. 37 (b), there is provided means for changing the direction of the link AA in the direction of the pivot O and a pressing spring U sandwiched between the link A and the rotating body J. There is a means for shrinking, but apart from this, means for applying resistance to the rotation of the rotating body J is employed. Even if these means are used singly, the door D is decelerated even if there is a difference in effect.
One means for applying resistance to the rotation of the rotating body J will be described. The arm Ab is rotatably supported around a rotation support shaft Ia provided at an intermediate portion of the link A, and the wheel BB is mounted on a rotation support shaft Ib provided at the tip 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.
As shown in FIG. 37 (b), the wheel BB enters the sliding surface KK in a direction perpendicular to the sliding surface KK, moves on the sliding surface KK in the parallel direction as shown in FIG. 37 (c), and the tension spring VV extends. Thus, 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 a 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.

Next, a damper that applies resistance to the rotation of the rotating body J will be described.
In FIG. 37, the structure of the damper is shown in a sectional view. The damper is mainly composed of a cylinder Sl and a piston Ps. The end of the cylinder Sl is rotatably supported around a support shaft Slw provided on the door frame W, and the end of the shaft Pss of the piston Ps is provided on the rotating body J. Connected to the support shaft Pssj. The opening at one end of the cylinder Sl is blocked by a sealing lid Sla, and the lid Slb having a through hole through which the shaft Pss passes is attached to the other end to allow the air to enter and exit. Cylinder
Sl is separated by a piston Ps into a sealed chamber Sli on the sealed lid side and an outer 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 is provided with a through-hole through which the shaft Pss passes in the center, and the piston Ps is mounted so as to be able to reciprocate along the shaft Pss. Pa per tip is provided at the tip of the shaft, and Pb is provided per intermediate portion at a position away from Pa per tip by a distance equal to or greater than the thickness of the piston. Piston Ps
Reciprocates between Pa per tip and Pb per intermediate part.

Pa per tip is a valve that shuts off the intake air to the sealed chamber Pli, and when the shaft Pss moves in the direction of being pulled out of the cylinder Sl, the piston Ps moves along the shaft Pss per tip.
It moves toward a and comes into close contact with Pa per tip, blocking the air in and out of the sealed chamber Sli and depressurizing the sealed chamber Sli.
Pb per intermediate portion is a valve that shuts off the exhaust from the sealed chamber Sli, and the shaft Pss is connected to the cylinder Sl.
When moving in the direction to be pushed in, the piston Ps moves toward the Pb per intermediate portion along the shaft Pss and comes into close contact with the Pb per intermediate portion, blocking the air in and out of the sealed chamber Sli. Pressurize Sli.

The link device shown in FIG. 27 is not limited to the link device shown in FIG.
By attaching a "simple damper that can never be said to be strong" and delaying the "switching means", the large impact acting on the door can be absorbed and mitigated. The big impact on the door means the impact caused by the collision at the end of every movement.
For example, in FIG. 1, if a support shaft connecting the end of the cylinder Sl in FIG. 37 is provided on the door D and a support shaft connecting the end of the shaft Pss of the piston Ps is provided on the support shaft, the link A is very slowly. It becomes a door to be sealed, and it also becomes a shock absorber using the door D as an impact absorbing portion.

As described with reference to FIG. 4, the “rotating mechanism in which the wheel B attached to the tip of the link A presses the sliding surface K at a substantially right angle” is small along the sliding surface K in the “range (ii)”. The force is converted into a large force in the direction of the axis line Za, and the door is sealed. In the “(A) range”, a direction along the sliding surface K while supporting a large force in the direction of the axis line Za of the link A. Therefore, it can be used as a moving means that moves while supporting a large weight in industrial fields other than doors.
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. This moving means is a moving means that rotates with a small force while supporting a large force in the axial direction, and has a feature that supports the weight of the object.

FIG. 38 explains the “rotation mechanism in which the wheel B attached to the tip end portion of the link A presses the sliding surface K at a substantially right angle” as in FIG. 4, and shows the drawing method of the shape of the sliding surface K . FIG. 4 shows a case where the sliding surface K is a concave surface, and FIGS. 38A and 38B show a case where the sliding surface K is a convex surface. FIGS.
If 8 (a) and (b) is the case where the rotation axis of the link A is inside the sliding surface K, FIG.
c) (d) is the case of outside. 38 (a) and 38 (c), the door frame W includes a pivot axis O and a connection axis C, the cam body KK includes a sliding surface K and rotates about the pivot axis O, and the link A has a wheel B at the tip. Is attached and rotated about the connecting shaft C. 38 (b) and (d) are respectively shown in FIG.
) (C) is an operation explanatory view. The action line of the force Fb that the wheel B presses the sliding surface K is shown in FIG.
) And (b) and a pivot axis O in FIGS. 38 (a) and 38 (c).

38 (b) and 38 (d), a circle Rb is a circular orbit of the contact point b between the sliding surface K and the wheel B,
A straight line T passing through each point bi (i = 1, 2, 3,...) Equally distributed on the circle Rb is an action line of a force Fb that the wheel B presses the sliding surface K. Virtual circle Ra and ai (i = 1, 2, 3,...
.) And a straight line T starting from each point bi (i = 1, 2, 3,...) Is represented by an arc Ri (i =
1, 2, 3,... Is a distance aib with ai (i = 1, 2, 3,...) As the center.
i (i = 1, 2, 3,...), and the wheel B is connected to each point bi (i = 1, 2, 3).
), The shape of the sliding surface K in the vicinity of the contact b is shown.
In FIG. 38 (b), the arc R4 passing through the point b4 and centering on the contact point a4 is represented by the cam body rotation axis Qk.
, The arc R5 and the arc R4 form one arc, and the start point b4 is the start point of the arc K4 that has been rotated and moved. Move to k4. 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 sliding surface KA. . In this way, the sliding surface K is obtained by successively continuing R5, K4, K3,.
A is drawn. The sliding surface KA in the figure is a sliding surface K that rotates about O, and is the sliding surface K when it contacts the wheel B at the point b5.
In FIG. 38 (d), when the wheel B is in contact with the sliding surface K and the contact bi (i = 1, 2, 3,...), The sliding surface continuous with the contact bi is “the action line Fb and the virtual. An arc Ri (i = 1, 2, 3,...) Centering on a contact point a ”with the circle Ra.
A circle Roi (i = 1, 2, 3,...) Is a circle that passes through the contact point bi with the pivot O as a center, and intersects the arc Ri at an intersection point ci (i = 1, 2, 3,...). When the arc bici divided by the circle Roi is sequentially rotated around the center of the axis O to be continuous with R0, one curve R0K1K2K3
... are formed. This curve is involute.

4 and 38A and 38B, the virtual circle moves and the shape of the sliding surface K changes depending on the position of the rotation axis of the link A. In FIGS. 38C and 38D, the center of the virtual circle is Since it is the rotation axis of the sliding surface K, the shape of the sliding surface K is determined by the size of the virtual circle Ra, and the point bi is a circle Ro1, Ro2.
, Ro3, “the line of action of the force Fb that the wheel B presses the sliding surface K and the pivot O
And keep a certain distance. In addition, regardless of any movement of the cam wheel B, the pressing force Fb applied to the wheel B is constant with respect to the “driving force acting around the pivot axis O”.
For example, when the rotating shaft of the wheel B supports the weight and the wheel B moves along the circular orbit as shown in FIG. 38C, the direction of the action line of the pressing force Fb changes, and the action line of the weight. As the direction force changes, the “driving force acting around the pivot axis O” is initially large when the wheel B moves, and is finally reduced to eight. If the wheel B moves on the vertical line, the line of action of the pressing force Fb always coincides with the vertical line, and when the wheel B moves, a constant force acts from the beginning to the end. Can minimize the maximum force required.

FIG. 39 is similar to FIG. 38 (c) (d) in the same manner as “the embodiment in FIG.
) Is used as a weight moving device in the vertical direction, and the lid D is used in FIGS. 39 (a) and 39 (b).
FIG. 40 is an elevation view for explaining the operation from the lying state shown in FIG. 39 to the standing state shown in FIGS. In the embodiment of FIG. 1, the action line of the pressing force Fb and the action line of gravity are parallel when the lid is nearly horizontal, and the action line of the pressing force Fb rotates and becomes not parallel as the lid is suspended. , FIG.
In this embodiment, the action line of the pressing force Fb and the action line of gravity are parallel in a large range.
The cam body KK has a sliding surface K on the outer edge portion, and is rotatably supported around a “connection axis C provided on a lid D that is rotatably supported around the pivot axis O”. Rotate in the direction to raise the lid D in the direction of arrow B in the figure. The carriage has a “contact surface KAA that is a friction surface in contact with the sliding surface K” on the upper surface.
And both ends are supported by wheels BB and move on a horizontal plane H to which the pivot O is attached. Contact surface KAA
The action line of the force Fb that presses the sliding surface K passes through the connection axis C through the “contact point b between the sliding surface K and the contact surface KAA” and in contact with the “imaginary circle Ra of radius r”. A constant distance r is maintained in parallel.

In FIG. 39 (a), the position on the contact surface KAA is ba0 and the position on the sliding surface K is bb0.
When the position bb0 is on a vertical line Z passing through the connecting axis C, as shown in FIG.
In b), the length of the outer edge portion of the sliding surface K that reaches the contact b and the position bb0 is longer than the “distance r between the vertical line Z and the contact b”, and the sliding surface K rotates in the direction of arrow a in the figure. By doing so, the carriage KAA moves in the direction of arrow C in the figure.
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 a large resistance to the rotation of the cam body KK. 39 (a) to 39 (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. 39 (e) to 39 (g). 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. 39 (a) shows an embodiment in which blades are applied to both the outer edge portion of the sliding surface K of the cam body and the contact surface KAA to engage with each other, but FIGS. 39 (b) and 39 (c) show the blades. This is an example that has not been applied.

In the state where the lid D is nearly lying down, the “distance between the gravity line of action and the pivot O” is applied to the rotation of the lid D.
Since the ratio of “Lw” and “distance Lf between the force action lines Fb and o” is substantially constant, the lid D is rotated by continuing to exert a substantially constant rotational force around the connection axis C, and the gravity center Can be raised. When the center of gravity rises in a state where the lid D is nearly lying down, the maximum value of the necessary force becomes smaller as the rotational force becomes more uniform.
FIG. 39D shows a relationship in which the cam bodies KK shown in FIGS. 39A to 39C are attached to each other, and “the action line Fb of the force with which the cam body KK presses the sliding surface H”. In FIG. 39 (d), it is on the side closer to the pivot axis O than the gravity action line Z and on the far side in FIGS. 39 (a) to 39 (c).
When the lid D transitions from the lying down to the standing state, the distance Lw between the gravity action line and the pivot axis O and the distance Lf between the force action line Fb and the pivot axis O are both decreased, but FIG. In d), the distance Lf approaches zero, and no matter how large the force Fb is, the force for rotating the lid D disappears. The lid D is not rotated at a position where the force action line Fb passes through the rotation axis Q as shown in FIG.
Throughout the entire process in which the lid D transitions from the lying down to the standing state, 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.
9 (a)-(c) approaches infinity. In the state where the lid D is almost upright, the force for rotating the lid D in the direction indicated by the arrow B in FIG.
Excess in c).

FIGS. 39 (e) and 39 (f) are obtained by attaching the spiral wheel described in Patent Document 12 instead of the cam body KK of FIGS. 39 (a) to 39 (c). Is formed by sequentially superposing right triangles whose radius is the radius of the virtual circle Ra,
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 determined by the radius of the virtual circle Ra in the same manner as the shape of the cam body KK in FIGS.
When the shape of the spiral wheel drawn by the same virtual circle is compared with the shape of the sliding surface K, FIG.
In the case of 9 (e) (f), the differential element of the spiral wheel is a line segment perpendicular to the radial direction.
This is because it is on the side farther from the connecting axis C than the differential element Ri of the arc shown in (d). As the contact point b moves away from the rotation axis C, the degree of convergence to a circle increases, more closely approximates a circle, and the increase of the rotation axis C accompanying the rotation of the cam body is small. In particular, at the beginning of the process in which the lid D shifts from the lying down to the standing state, the rotation axis C rises with the rotation of the cam body shown in FIGS. 39 (a) to 39 (c).
The rise of the rotating shaft C accompanying the rotation of the cam body in (f) is drastically reduced as soon as the cam body starts to rotate.
Thus, the curved glands drawn by the same virtual circle are clearly different, and FIGS. 39 (a) to (c)
The shape of the sliding surface K is an involute curve, and the curves in FIGS. 39 (e) and 39 (f) are not involute curves.

The two opening / closing bodies D and W rotate relative to each other with the pivot O as an axis. The operation of fixing one of the two opening / closing bodies D and W and rotating the other around the pivot O as an axis is In other words, when viewed from the other side, the other side is fixed and one side rotates about the pivot axis O. For example, in FIG. 4 and FIG. 38, the other rotating around O is the door D or the sliding surface K, and the one fixed is the door frame W, which is the paper surface. When the other door D or the sliding surface K is fixed, one of the door frames W, which is a paper surface, rotates around O as an axis.
FIG. 40 is an operation explanatory view in which the cover K is fixed in FIG. 4 and one side of the paper frame, which is the door frame W, rotates about O as an axis. The characteristic that when the sliding surface K is pressed in a substantially right angle direction, the rotating shaft of the wheel supports a large force that is easy to move even if the force substantially parallel to the sliding surface K is small and that is substantially perpendicular to the sliding surface K. " Is applied to the lid that stands up and down.

In FIG. 40A, “the link A for attaching the wheel B to the rotation axis Ib of the wheel at the tip portion” is rotatably supported around the “connection axis C provided on the lid D”. The lid D rotates about the pivot O fixed to the fixing portion W, and the axis of the pivot O is horizontal. The lid D0 indicates the standing state, and indicates the state where the “rotational moment Mo around the pivot axis O due to the gravity of the lid door D” is the smallest. The lid D3 indicates a lying state, and indicates a state where the “rotational moment Mo around the pivot axis O due to the gravity of the lid D” is the largest. The rotation moment Mc acts on the connecting shaft C around the connecting shaft C in the direction indicated by the arrow A in the figure by the urging means (not shown), and the rotation moment Mc opposes the rotation moment Mo to keep the lid D stationary.

40 (a) and 40 (b) are elevational views for explaining the operation in which the wheel B moves along the sliding surface K in the direction of arrow A in the figure and the lid D rotates in the direction of arrow B in the figure. In the range where K is almost horizontal, the shape of the sliding surface K approximates to an arc. Therefore, in FIGS. 40A and 40B, when the shape of the sliding surface K is an arc, the center of the arc is set to the virtual point Q. The action line of “the force Fb that the wheel B presses the sliding surface K” passes through the “contact point b between the wheel B and the sliding surface K”, the wheel rotation axis Ib, and the virtual point Q. Unlike the case of FIG. 4, the “intersection angle Θf between the link A and the vertical line on the sliding surface K” varies depending on the position of the wheel B.
40 (c) and 40 (d) show, instead of “link A and sliding surface K in FIGS. 40 (a) and 40 (b)”, “rotating body J that rotates about a fixed support shaft Sw provided on fixed portion W. ”And“ Link A connected to the rotating body J and connected to the lid D ”. In FIGS. 40 (a) and 40 (b), the rotating shaft I of the wheel is attached.
Since b moves circularly around the virtual point Q, the “force Fb that the wheel presses the sliding surface” shown in FIGS. 40A and 40B acts on the axis of the rotating body J, and the fixed support shaft Sw. Act on.

FIG. 40A is an operation explanatory diagram in which the lid D and the link A shift from an orthogonal state to an overlapping state. As the wheel B approaches the pivot O along the sliding surface K, the lid D rises and is linked. A moves slightly horizontally from the vertical state. While the link A is maintained in a substantially vertical state and substantially parallel to the line of gravity, the wheel B moves along the sliding surface K with the “circumferential force of a small circular motion” and moves to the axis of the link A.
Supports the radial force of large circular motion. Also, the intersection angle Θ between the link A and the line of action of the force Fb
f increases. The rotational moment Mc is transmitted to the “force acting on the axis of the link A” and the lid D
This corresponds to the decrease in the “rotational moment Mo around the pivot axis O due to the gravity of the lid door D” as 0 stands.
If the sliding surface K of the arc is movable without being fixed, the “intersection angle Θf between the cam wheel rotating body Jg and the normal standing on the sliding surface K” is set to the position of the wheel B on the sliding surface K, or Depending on the opening degree of the lid D, the action line direction of the pressing force Fb can be designed in a desired direction. When the arcuate sliding surface K is rotated about a support shaft to which the arc is not fixed, the sliding surface K is not limited to the arc but has a free shape.
It is the same as when is fixed.

Further, when the sliding surface K is fixed so as to correspond to the change of the “rotational moment Mo around the pivot axis O due to the gravity of the lid door D” by moving the sliding surface K having a fixed shape without being limited to rotation. However, by changing the shape of the sliding surface K, it is possible to cope with the change in “the rotational moment Mo around the pivot axis O due to the gravity of the lid door D”. FIG. 40B is an operation explanatory view after moving the sliding surface K, and the rate at which the intersection angle Θf increases is small. Thus, by moving the sliding surface K without being limited to rotation, it is possible to make the crossing angle Θk as constant as possible according to the position of the cam wheel, and even when the lid D stands up, the pivot O It is possible to maintain a balance of moments around.
40C and 40D respectively correspond to FIGS. 40A and 40B, and what can be said about FIGS. 40A and 40B is also true of FIGS. 40C and 40D. If the fixed support shaft Sw is movably attached, or if the length of the rotating body J changes, for example, when the connecting point of the surrounding pair is a sliding pair, the degree of freedom of the link device increases, and the link device moves. It can be freely adjusted, and further desired balance is achieved by changing the spring force. Further, the link A is rotated with a small force while supporting a large force so that the axial line Za of the link A and the force acting line are close to each other.

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 Push spring V Pull spring W Fitting or plate to be attached to door frame

Claims (6)

A "opening / closing body comprising two links" and a "rotating part comprising one or more links" that rotate relative to each other while sharing the pivot axis O, and "the connecting shafts at both ends of the above-mentioned stretching part" are the two links. Each of the links is connected with a pair or a slip pair to form a link device, and a driving torque Mv acting around the “drive connection shaft other than the pivot O” of the link device is transmitted. With the opening and closing device that opens and closes the opening and closing body, the rotational force Mo works around the pivot axis O,
A link A rotatably supported around a connection axis C provided on one of the two links includes a slurder B that moves along a groove Ka provided on the other of the two links, and the groove Ka The direction in which one of the two links rotates about the pivot axis O by the pressing force Fb acting between the slurder B and the slurder B, and the one of the two links is pivoted by the axial force acting on the link A. A switchgear characterized by being opposite to the direction of rotation about the axis. A first support provided in one of the two links in an area sandwiched between the “two links” and the “opening / closing body composed of two links” sharing the pivot O and relatively rotating. A first door that is pivotally supported around the shaft and is provided between "one of the two links" and the first door, and biases the first door. A spring between the biasing means, the first door, and "the other of the two links";
The first urging means is an opening / closing device that rotates "the other of the two links" about the pivot O through the first door and the spring,
The first urging means has a force for rotating “the other of the two links” about the pivot O and a force for the spring to rotate the “the other of the two links” about the pivot O. Opening and closing device characterized by acting alternately. "Opening / closing body consisting of two links" sharing the pivot axis O and relatively rotating, and a link A provided with a slurder B rotatably supported around a connection axis C provided on one of the two links, An opening / closing device that includes a groove Ka provided on the other of the two links, and wherein the slurder B moves along the groove Ka to open and close the opening / closing body,
An opening / closing device, wherein the force that rotates the other of the two links about the pivot O is a force that moves the slurder B away from or closer to the pivot O. A "opening / closing body comprising two links" and a "rotating part comprising one or more links" that rotate relative to each other while sharing the pivot axis O, and "the connecting shafts at both ends of the above-mentioned stretching part" are the two links. Each of the links is connected to each other by a pair or a slip pair to form a link device, and a force F acts on one of the operating points of the switch to open and close the switch so,
The “(A) range” where the rotational force Mo is small, the “(A) range” where the rotational force Mo is large, and the “Switch” that switches from the “(A) range” to the “(A) range”. A switching device, wherein the line of action of the force F passes through the pivot O or the vicinity thereof in the “switching range”. A "opening / closing body comprising two links" and a "rotating part comprising one or more links" that rotate relative to each other while sharing the pivot axis O, and "the connecting shafts at both ends of the above-mentioned stretching part" are the two links. Each of the links is connected with a pair or a sliding pair to form a link device, and a traction force that moves the “drive connection shaft that is not pivotal O” of the link device works to make the opening and closing body An opening and closing device that opens and closes
Traction force is transmitted by a string moving along a pulley, and the cross-section of the string is deformed when moving along the pulley. A "opening / closing body comprising two links" and a "rotating part comprising one or more links" that rotate relative to each other while sharing the pivot axis O, and "the connecting shafts at both ends of the above-mentioned stretching part" are the two links. Each of the links is connected with a pair or a slip pair to form a link device, and a driving torque Mv acting around the “drive connection shaft other than the pivot O” of the link device is transmitted. With the opening and closing device that opens and closes the opening and closing body, the rotational force Mo works around the pivot axis O,
The opening / closing apparatus characterized in that the “driving connecting shaft other than the pivot O” is movably attached to one of the opening / closing bodies.

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