JP2015206219A - Reduction gear automatically releasing resistance - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a door that is gently and fully closed by comprising not a door closer with a high-pressure container but small resistance means, and provide a reduction gear that does not damage a dwelling environment and that can be miniaturized.SOLUTION: A device for decelerating a door is operated by a spring different from a spring for urging the door. Even when a weak spring is adopted, either the device for decelerating the door or a device for urging the door is operated, and the door is necessarily put into a fully closed state without being kept in a stopped state even in the case where the door is stopped midway through a closing operation. Resistance acting on the door is automatically removed after deceleration, and the spring decelerating the door is restored to inhibit rotation in a door opening direction.

Description

The present invention relates to a reduction gear that automatically releases resistance.

Since the pivot axis O is vertical and the potential energy of the door D rotating around the pivot axis O does not change, the strain energy of the spring is converted to the kinetic energy of the door without being reduced, and the door that has started to close is subsequently accelerated. Follow one by one. If resistance is applied to the movement of the link device and the resistance does some work, the kinetic energy of the door decreases and the door decelerates, but if friction resistance is used for the resistance, The door will stop and the door will not move again. When the frictional resistance is small, the door cannot be decelerated, and when it is fully closed, it collides violently with the door frame and generates a loud impact sound.

The door closer with a hydraulic cylinder adopts the viscous resistance of the fluid that passes through a small hole to the above resistance, the viscous resistance of the fluid resists as the door turns faster, and if the door stops, it will not resist It is a resistance that prevents the door from being accumulated even if it stops midway.
However, a door loaded with frictional resistance or fluid viscosity resistance will not rotate unless the spring force is increased beyond the frictional resistance or fluid viscosity resistance, so there is a drawback that the door feels heavy when the door is opened. is there.

Patent Document 1 relates to a door closer that rotates a door with a minimum necessary force so that a large force is not required when opening a closed door. The door is rotated with a small amount of spring distortion energy as much as possible. The door is prevented from accelerating.
As long as the force continues to act on the door of Patent Document 1, it is natural to continue to accelerate, but quietly fully close. The reason is that as the door is fully closed (hereinafter referred to as “when fully closed”), the air resistance acting on the door increases and the door decelerates, and when the door is fully closed, it disappears without permission. It is.
The door of Patent Document 1 is easily affected by air resistance, and has a drawback that when the room window is opened, particularly on a high floor, the door may suddenly close and an accident may occur.

With reference to FIG. 1, Patent Document 1 will be described.
At the time of latch contact, when the latch Rt provided on the door D contacts the door frame W (hereinafter referred to as latch contact), not only the force to rotate the door but also the force to dent the latch is required. Before the contact, only the force Fv for urging the door acts, and after the latch contact, a force (hereinafter referred to as a fully closing force) that rotates the door while the latch is depressed acts. In the door of Patent Document 1, the action line of the force Fd acting on the door suddenly moves greatly when the latch contacts, and the distance Lf between the action line of the force Fd acting on the door and the pivot axis O of the door suddenly increases. To feature.

In the link device in which the door and the door closer are interlocked, the door closer is rotated by the door simultaneously with the rotation of the door by the door closer. In the door of Patent Document 1, the force of the spring biasing the door is small in the latch contact range, and a large force acts on the door. That is.
If the door closer suddenly stops and the door continues to move due to dynamic inertia, the door closer brakes the door. By simply stopping or slowly rotating the door closer of Patent Document 1, the door that continues to move with dynamic inertia (hereinafter referred to as door inertia force) is braked or decelerated.

In this case, the force required to brake or decelerate the door closer is much smaller than the force required to directly brake or decelerate the door that continues to move due to dynamic inertia. The resistance required to stop or slowly rotate the door closer of Patent Document 1 is much smaller than the resistance of a door closer equipped with a normal hydraulic cylinder, and the device can be made smaller.

In FIG. 1, the force by which the door rotates the door closer works in the axial direction of the rotating body J, and the rotating body J rotates with a small force even while supporting a large door inertia force in the axial direction. On the other hand, in a door closer equipped with a normal hydraulic cylinder, the door inertia force acts not in the axial direction of the link but in the rotational direction, and a force greater than the door inertia force is required to rotate the link. A spring will be built in.
Since the springs are restored in an instant, the door will not rotate slowly unless the springs are restored slowly. The larger the built-in spring, the slower it will rotate unless a large resistance is applied. If a large resistance is applied, it is necessary to incorporate a larger spring, and incorporating an extremely large spring is a drawback of a door closer equipped with a normal hydraulic cylinder.

Japanese Patent No. 4690350

If a resistance device that performs the same function as “the air resistance that starts and stops without permission” can be attached to the door of Patent Document 1, the door is silently fully closed in any case. The question is whether to reproduce the same effect as air resistance in the following to act on the door.
Fundamentally, the question is “How to restore the spring slowly”, and to slow down, “How to convert kinetic energy into heat loss and strain energy and reduce it” is the issue. is there.

In the link device of Patent Document 1, as shown in FIGS. 1, 2, and 6, a rotating body J is rotatably supported around a connection axis C provided on a door D and works around the connection axis C. The force F is transmitted to the door D via the contact b or the connecting shaft P, and “the connection axis C where the line of action of the force F passing through the contact b or the connecting shaft P is the rotating shaft of the rotating body J”. It keeps moving with a small force, supporting a large door inertia force while maintaining a “passing state near”. The force action line F moves away from the vicinity of the connection axis C, and the force F is not transmitted to the door D. The contact b or the connecting shaft P can move with a small force in a direction substantially perpendicular to the force acting line F.
The fact that the rotating body J supports a large door inertia force and continues to move with a small force means that the rotating body J can be rotated slowly by applying a small resistance to the rotating body J, and the rotating body can be rotated slowly. It means you can do it.

As the small resistance attached to the rotating body J, the resistance of the resistance means Rj3 shown in FIG. 2 is appropriate. Similar to the air resistance acting on the door surface, the viscosity resistance of the fluid passing through the slit increases according to the magnitude of the door inertia force and disappears when the door inertia force disappears.
“The one container Sp1 and the other container Sp2 are elastic bodies whose capacity is restored to their original state, and the one container Sp1 and the other container Sp2 have a constant capacity of the fluid filled in the container Sp. It is a spoid made of an elastic film to be restored, and is connected to share the inlet / outlet Sl, and the fluid Fl discharged from the one container Sp1 contracted without leaking from the inlet / outlet Sl is expanded while the other container Sp2 is expanded. The fluid Fl contained in the other container Sp2 is returned to the one container Sp1, and the viscous resistance of the fluid Fl passing through the entrance / exit Sl is resistant to the expansion and contraction of the one container Sp1 and the other container Sp2. It is characterized by. "

Even if the viscous resistance of the fluid Fl is not adopted, the “decelerator that is driven by power different from the means for energizing the door and automatically releases the resistance” is similar to the air resistance acting on the door surface. The door largely resists according to the magnitude of the door inertia force, and when the door inertia force disappears, it resists.
“The moving body S described in FIG. 5 moves at a low speed, contacts and separates from the moving body D moving at a high speed in the same direction via the contact b, and decelerates the moving body D relatively integrally. The moving body S is moved by power different from the means for energizing the moving body D, and the resistance for decelerating the moving body S indirectly acts on the moving body D via the contact point b with the moving body S. The contact b is moved relatively in a direction substantially perpendicular to the line of action of the force passing through the contact b. "

The moving body D and the moving body S are compared to the door D shown in FIG. 3 and the sliding surface KK shown in FIG. 3. In FIG. It moves relatively at right angles, and supports a large door inertia force and continues to move with a small force. The moving direction of the moving body D is the direction of the action line of the pressing force Fk, and the moving body S moves relatively in a direction substantially perpendicular to the direction of the action line of the pressing force Fk, and supports a large door inertia force and a small force. Keep moving on.
It moves along the sliding surface KK slightly inclined from the direction perpendicular to the direction of motion of the wheel B shown in FIG. The effect is the same even if the wheel B moves along the sliding surface KK, and the moving body S moves relatively in a direction substantially perpendicular to the direction of the line of action of the pressing force Fk.
The moving body D contacts the moving body S at the contact point b, and moves relative to the direction of movement of the contact point b while preventing the movement of the contact point b in the movement direction. The contact b moves in a direction substantially perpendicular to the line of action of the force passing through the contact b.

The decelerating resistance is a resistance that acts on the movement of the moving body S by increasing the number of times the moving body S collides by repeatedly stopping and moving, and indirectly decelerates the moving body D via the moving body S. The kinetic energy of the moving body D that moves relatively integrally with the moving body S is deprived of the heat generated at the time of collision, and the moving body D decelerates. As illustrated in FIG.
The moving body S moves along a predetermined track Zm provided in the fixed portion W and pulls the wheel B. The link A is provided on the moving body S and is rotatably supported around the connection shaft C. The wheel B is mounted on the wheel support shaft Ib provided at the tip, and the wheel B is a track K provided on the fixed portion W. Move along. The track K is characterized by comprising a track KK that causes the wheel B to revolve around the stop position of the connecting shaft C.

As illustrated in FIG.
“A wheel B that moves along a groove M provided in the door D and in a direction substantially perpendicular to the direction of movement of the door D moves along a sliding surface K and a sliding surface KK provided in the fixed portion W. The sliding surface KK is provided in a direction substantially perpendicular to the direction of movement of the door D. "
11 and 13, the wheel B moves along the track KK. Even if the track KK moves along the wheel B, the track KK moves relatively along the wheel B. The moving body S that pulls the wheel B is also the moving body D shown in FIG. 5 that supports the dynamic inertia force on the track KK via the wheel B.
3, 11, and 13, the solving means is the same as the solving means in FIG. 5, and the contact b moves in a direction substantially perpendicular to the line of action of the force passing through the contact b.

In this way, the speed reduction mechanism in which the moving body S repeatedly stops and moves converts kinetic energy into heat loss at the time of collision. The speed reduction mechanism described in FIG. 22 converts kinetic energy into spring strain energy. The spring is restored to prevent the door from bouncing back.
“Equipped with a biasing spring that biases the rotation of the door D, a deceleration spring that decelerates, a check device that enables driving and idling, and a resistance release device. , A reduction device that decelerates the door D during expansion and contraction and does not transmit the restoring force during restoration. It is characterized by moving in a direction substantially perpendicular to the supporting direction. "

The direction in which the restoring force of the spring is supported is the rotational direction of the door D, and is the direction of movement of the contact b shown in FIG. Also in FIG. 22, the solution means is the same as the solution means in FIG. 5, and the contact b moves in a direction substantially perpendicular to the line of action of the force passing through the contact b. The dynamic inertia force of the moving body D is transmitted to the moving body S via the contact point b. The dynamic inertia force of the moving body D is supported by the connecting shaft C in FIGS. 5 and 11 and the sliding surface KK in FIGS. 3 and 13. In FIG. 22, the action line of the force F passing through the contact b is connected. By moving away from the axis C, the dynamic inertial force (spring restoring force) of the moving body D is not supported.

The speed reducer shown in FIG. 3, FIG. 5, FIG. 11, FIG.
`` Means that move at low speed and come into contact with and disengage from moving body D moving at high speed in the same direction, decelerating moving body D together with moving body D, and energizing moving body D '' A device that is driven by another power and decelerates the moving body S is provided, and a resistance that decelerates the moving body S acts on the moving body D through the contact b, and the contact b is substantially an action line of force passing through the contact b. A speed reducer characterized by moving in a right angle direction. "

It goes without saying that the present invention will contribute not only to the door but also to other industrial fields so that the door of the present invention can be replaced by all moving bodies having speed and mass. There are a plurality of means provided by the present invention, which coincide with each other for the purpose of quietly closing the door quietly. Contribute independently. Each means is an independent claim and not a dependent claim.

By simply attaching a small resistance to the door closer of Patent Document 1, the door closer of Patent Document 1 is not turned by the door. Explanatory drawing of the small resistance means attached to the door closer of patent document 1

Explanatory drawing of the speed reduction means that employs the resistance of air passing through the slit (in the case of a slip pair) Explanatory drawing of the speed reduction means that employs the resistance of the fluid passing through the slit (in the case of turning pair) Explanatory drawing of retreating full closure prevention means Illustration of a link device that moves even when the door stops Explanation of the mechanism where a moving body moving at low speed decelerates a moving body moving at high speed Explanatory drawing of a fully-closed device provided with a rotation preventing means that moves backward Explanatory diagram of resistance that works in the time when the door and the door closer are not interlocked Illustration of resistance acting on the door in the switching range Explanatory drawing of the mechanism that converts small movements into pendulum motion and decelerates Illustration of a gear mechanism that converts a small operation into a large operation and decelerates

A moving body that moves at a low speed moves while contacting a moving body that moves at a high speed, and decelerates the moving body. The moving body pulls a wheel that moves along a predetermined trajectory and repeatedly stops and moves. Of the mechanism that moves at low speed

Explanation of the mechanism where the wheel moves along the revolution track and the moving body stops at the center of revolution Explanatory drawing of the moving body towing a plurality of wheels B moving along the revolution trajectory Explanation of the mechanism in which the force to urge the door and the force to decelerate the door work alternately and repeatedly Explanatory drawing of a moving object that keeps stopping for a long time Illustration of a moving body that moves with amplitude

Explanatory drawing of a spring that does not return to the opening direction even if it is restored by decelerating the door by expanding and contracting, with a reduction device that converts the kinetic energy of the door into the strain energy of the spring

Resistor release mechanism explanatory diagram that stops spring restoration and starts to move in no load condition Explanatory drawing of the mechanism that releases the resistance away from the door by the restoring force of the spring Illustration of a check device that decelerates the door during expansion and contraction and does not convey the restoring force during restoration Explanatory drawing of a one-way clutch that does not reversely rotate after decelerating the door When the door stops, the mechanism will be released. Explanatory drawing of the mechanism where the spring that decelerated the door is restored and the door starts to close Explanatory drawing of the mechanism for releasing resistance so that the operation differs between when the spring is expanded and contracted Explanatory drawing of the mechanism that releases the resistance when the pinion is detached from the rack Explanatory drawing of door closer that moves slowly in full closing time from immediately before full closing

Explanatory drawing of a door closer equipped with a speed reducer that reverses G when blocking the rotation of the door

Explanatory drawing of a hinge with a spring that biases the rotation of the door and a spring that decelerates

Drawing explaining other application examples

Explanatory drawing of the loading platform that moves up and down in balance regardless of the weight of the luggage Explanatory diagram of the elevator that eats on the pillar and does not leave Illustration of a revolving door that does not die between the door and the door frame

FIG. 1 is an explanatory diagram of the link device shown in Patent Document 1. The link device is a fixed portion W (or a door frame W, which is the fixed portion W on the drawing sheet), a door D, and a rotating body J. It consists of three links. The door D and the rotating body J are pivotally supported around a pivot axis O provided on the fixed portion W and a connection axis C provided on the door D, respectively, and are supported on a wheel supporting shaft Ib provided at the tip of the rotating body J. Wheel B is mounted. The fixed part W is provided with a pivot O, a door frame W, a sliding surface K, and a reduction sliding surface KK, and the wheel B moves along a groove sandwiched between the sliding surface K and the reduction sliding surface KK. To do. The rotating body J is connected to the door frame W through the wheel B and the sliding surface K in a sliding pair.
The rotating body J is urged by the urging means V (the pulling spring V in the figure), rotates around the connecting shaft C in the direction of arrow A in the figure, and the wheel B moves along the sliding surface K from the start end 1. Moving toward the terminal end 3, the door D rotates around the pivot axis O in the direction of arrow B in the figure.

Hereinafter, the wheel B is a general term for sliders that move along the sliding surface K, and the sliding surface K and the sliding surface KK are also rotating bodies that include the sliding surface K and the sliding surface KK at the outer edge, respectively. I will decide. The suffix of each symbol means the rotation angle Θd of the door D. For example, D30 indicates the state of the door D when the rotation angle Θd is 30 degrees. D90 indicates a door that is stationary at a fully opened position, and D0 indicates a door that is stationary at a fully closed position. At the position of the door of D80, the force for biasing the door reverses from the opening direction to the closing direction.
The pivot O, the door D, and the fixed part W (door frame W) are referred to as an opening / closing part, and the part other than the opening / closing part of the connecting shaft C, the rotating body J, the wheel B, and the sliding surface K is referred to as an expansion / contraction part or door closer. .

When the door D contacts the door stop Gw1 provided on the door frame W and is fully opened, it is hereinafter referred to as fully opened. When fully closed by contacting the door stop Gw2, it is hereinafter referred to as fully closed. The time immediately before the door is fully closed is hereinafter referred to as just before the door is fully closed. As shown in FIG. 1A, when the door is in the position from the fully open position to the position immediately before the fully closed position (hereinafter referred to as (A) range), the wheel B is in the vicinity of the pivot axis O within the (A) range. As shown in FIG. 1B, when the door is located from the position immediately before the fully closed position to the fully closed position (hereinafter referred to as the range of (i)), as shown in FIG. I) far away from Axis O. The boundary between the range (a) and the range (ii) is referred to as a switching range.
The line of action of the force Fd acting on the door passes through the contact point b between the wheel B and the sliding surface K and the wheel support shaft Ib. In FIG. 1A, when Θd = 80, the action line of the force Fd passes through the pivot axis O, and the action line of the force Fd reverses the direction in which the force Fd urges the door D when the axis crosses the pivot axis O. The direction in which the door D is urged is the direction in which the door D is pressed against the door stop Gw1 when Θd = 90 (hereinafter referred to as the opening direction), and the door D approaches the door stop Gw1 when Θd <80. Direction (hereinafter referred to as the closing direction).

The distance Lf between the line of action of the force Fd and the pivot axis O is small in the range (A), increases rapidly from the switching range, and is large in the range (I). The force of the pulling spring V acts on the door in the range (A) and relaxes as it approaches the fully closed state, but acts on the door in the range (A). The range of (ii) is small, and a large force acts on the door suddenly at the moment when the rotation of the door is small. The door of Patent Document 1 includes means for restraining the distance Lf to be small within the range (A) and means for releasing the restraint within the switching range.
As shown in FIG. 1B, when the latch male part Rd contacts the latch female part Rw (hereinafter referred to as latch contact), the force Fd acting on the door not only rotates the door but also latches. The force that dents the male part inside the door is necessary and is maximized.

The acting line of the force Fd acting on the door is in the range of (A), and is the axis core line Zj of the rotating body J (a straight line passing through the connecting shaft C and the wheel support shaft Ib (hereinafter, passing through the connecting shafts at both ends of the link). A straight line is referred to as an axial center line Z.) The crossing angle with the axial center line Z is large, and is substantially a right angle in Fig. 1 (a). In (a), the force Fd of the spring that rotates the rotating body J is transmitted to the door D more greatly as the crossing angle between the line of action of the force Fd and the axis Zj of the rotating body J is smaller.

The curve of the sliding surface K (ii) is a curve in which the distance Lc between the action line of the force Fd and the connecting shaft C is substantially constant, as described in Patent Document 1, and the action line of the force Fd. Is a curve that is always in contact with a virtual circle Rc having a radius Lc centered on the connection axis C.
The feature of the door closer of Patent Document 1 is that the range in which the distance Lc operates while maintaining a substantially constant state is large. As the distance Lc is smaller, the rotating body J is less likely to rotate even if the force Fd is large. Further, the smaller the distance Lc, the closer the curve of the sliding surface K (I) becomes to a circle, and the rotation of the door D is slight even if the rotating body J rotates greatly.

When the door and the door closer are linked, the door closer rotates the door and the door simultaneously rotates the door closer. In addition to the force of the door closer rotating the door, a dynamic inertia force acting on the door (hereinafter referred to as door inertia force) acts on the door, and when the door accelerates, the door closer is also accelerated. In the range of (ii), the door closer does not rotate the door, so it rotates rapidly in a state close to no load and operates greatly, but the operation ends in an instant.
In the range of (ii), a small force that rotates the door closer is converted into a large force and acts on the door to rotate it. However, even if the door is rotated with a large force at the same time, it is not turned if a small resistance is applied to the door closer. When resistance acts on the door closer and slowly turns it, the door will be in a position to turn the door closer and slow down without being able to turn the door closer.

Consider the case where the door is in a position to turn the door closer. In the range that occupies most of the rotation range of the door, the crossing angle between the line of action Fd that the door rotates the door closer and the axis Zj of the rotating body J is substantially perpendicular, and the door closer can be easily rotated by the door. Be made. Even if the resistance Rj1 acting on the door closer is large, the force to decelerate the door is small.
In the range where the rotation of the door is slight, the crossing angle between the acting line of the force Fd for rotating the door closer and the axis Zj of the rotating body J is substantially zero, and the door closer can be easily rotated by the door. Absent. Even if the resistance Rj1 acting on the door closer is small, the force to decelerate the door is large.

The feature of the door of Patent Document 1 is that the entire rotation range of the door from the fully open state to the fully closed state is a rotating body even if the door D rotates greatly with the position of the switching range immediately before the door D is fully closed as a boundary. It is distinguished from the range in which J rotates slightly (a) and the range in which the door D rotates slightly even if the rotating body J rotates greatly, and most of the rotation of the door closer J is This is to be executed in the range of (i) while the door slightly rotates from immediately before full closure to when full closure.
The door of patent document 1 expands the small movement of a door to the big movement of a door closer in the range of (ii). The fact that the door closer hardly moves in the range of (A) and moves greatly in the range of (I) means that the door closer can decelerate in the range of (Yes) and decelerates the door only in the range of (Yes). .

Even if the door of Patent Document 1 moves greatly within the range (A), the operation of the door closer is small. In the range of (ii), the door closer moves greatly while the door moves slightly. Even if the operation of the speed reducer incorporated in the door closer reaches the entire range including the range (A), the speed reduction device operates greatly to decelerate the door only in the range (Yes).
When the door closer of Patent Document 1 is a door closer provided with a hydraulic cylinder or is electrically driven and rotates at a low speed, the door rotates more rapidly in the range of (A) than in the range of (A). Become. The kinetic energy of the door is absorbed by the door closer that rotates at a low speed.

The decelerating means Rj1 converts the rotational motion of the rotating body J into the linear reciprocating motion of the piston Ps, and discharges the air Fl inside the cylinder S from the gap between the cylinder S and the piston Ps to the outside of the cylinder. The higher the linear motion speed, the greater the air viscous resistance acts on the air discharged to the outside, and the greater the resistance of rotation of the rotating body J.
The resistance applied to the rotation of the rotating body J is small in the range where the rotating body J is small and rotates slowly and the piston Ps moves slowly (A), and the rotating body J rotates large and fast and the piston Ps moves fast (Yes). Great in range. When the door is decelerated, the resistance is reduced by the slow movement of the piston Ps, and disappears when the door substantially stops. When the door stops, the door inertia force disappears and the door rotates without resistance.

The range of (ii) is a range in which the door D rotates small even if the rotating body J rotates largely. This is a range in which a large force acts on the door D even if the force for rotating the rotating body J is small. Equivalent to being.
The state in which the door and the door closer are interlocked is a state in which the door closer is turned to the door closer at the same time as the door closer is turned, and the rotating body J rotates greatly in the range of (ii) and a large force acts on the door D. This means that even if the door closer is rotated by applying a large force to the door, it is difficult to move.

Since the spring urges the rotating body J without loosening, the force continues to act on the door, the door accelerates and does not decelerate. Although the inertial force of the door increases, when the rotating body J rotates smoothly by the speed reduction means Rj1, the wheel B moves away from the sliding surface K and decelerates facing the sliding surface K as shown in FIG. It moves along the sliding surface KK. The door inertia force is a force by which the wheel B presses the sliding surface KK, and is supported by the sliding surface KK.
The door inertia force disappears when the door stops, and when the wheel B does not press the sliding surface KK, the wheel B returns to the sliding surface K by the force of the pulling spring V and urges the door. The wheel B closes and rotates the door while swinging between a track moving along the sliding surface K and a track moving along the sliding surface KK.

The axis core line Zj of the rotating body J is a straight line passing through the wheel support shaft Ib and the connecting shaft C. The door inertia force is a force by which the wheel B presses the deceleration sliding surface KK, and is supported by the rotating body J and acts as a force that decelerates the door D. The door inertia force is broken down into a force along the axis Zj of the rotating body J and a force along the sliding surface KK. The former is a force that acts on the connecting shaft C and resists rotation in the closing direction of the door, and the latter is a force that rotates the rotating body J and is a force that the door turns the door closer.
In the range of (ii), the closer to the tangential direction of the circle centering on the connecting axis C and the moving direction of the wheel B along the sliding surface K, the more perpendicular the moving direction of the wheel B is to the axis Zj of the rotating body J. As a result, most of the inertial force of the door works at right angles to the sliding surface KK, and the force for rotating the rotating body J is small.

When the door closer rotates smoothly, the door closer decelerates the door. Most of the inertial force is a force that turns the rotating body J. When a normal door closer that does not have the range (ii) rotates with a spring built into the hydraulic cylinder, the hydraulic cylinder resists most of the door inertia, so the hydraulic cylinder should withstand high pressure and not leak oil. There must be. Hydraulic cylinders need to be made rugged and the equipment is large.

As shown in FIG. 1, the door closer and the door frame W have the effect of greatly reducing the speed of the door that rotates at a high speed with the increased door inertia force by simply applying a small resistance to the rotation of the door closer so as to move slowly. It is recognized not only when and are connected by a slip pair, but also by a turn pair shown in FIG.

FIG. 2 is an operation explanatory view of a link device in which a connecting shaft P provided at the tip of the rotating body J and a fixed support shaft Sw provided on the door frame W are connected by a link A. The rotating body J is connected to a connecting shaft C. The door D rotates about the pivot O in the direction indicated by the arrow B in the figure. 2A is a state diagram in the range of (A) where the connecting shaft P is in the vicinity of the pivot axis O, FIG. 2B is a state diagram of a switching range in which the connecting shaft P starts to move away from the vicinity of the pivot axis O, FIG. (C) shows a state diagram in the fully closed state in a range where the connecting shaft P is far away from the pivot axis O. In the range of (i), the rotation of the door is small and the rotating body J rotates greatly.

The axial center line Zj of the rotating body J is substantially parallel to the door surface in the range (A) and substantially perpendicular to the door surface in the range (A). As the axial center line Zj of the rotating body J and the axial center line Za of the link A approach each other, most of the door inertia force works along the axial center line Za of the link A. When the door closer rotates the door, a pulling force acts on the link A, but when the door rotates and the door rotates the door closer, a compressive force acts on the link A, and the door inertia force is supported by the fixed support shaft Sw. Is done.
When the angle Θaj between the axis line Zj and the axis line Za of the link A is large, the force acting along the axis line Za rotates the rotating body J in the direction of arrow A in the figure, but when the angle Θaj is small, Do not rotate. The rotating body J can continue to rotate with a slight force while supporting a large door inertia force.

As shown in FIG. 2 (c), the only feature of the door of Patent Document 1 is that the connection shaft C is close to the fixed support shaft Sw when fully closed. When the connection shaft C is not close to the fixed support shaft Sw when fully closed, the angle Θaj remains large and does not decrease as shown in FIG. Rotate without resistance. The door closer hardly decelerates to the door inertia force.
In FIG. 2C, when the rotating body J and the link A are both substantially perpendicular to the door surface when fully closed and the angle Θaj is small, the rotating body J rotates against the door D. Even if the door is pushed strongly both in the opening direction and in the closing direction, it hardly moves. The door closer resists the large inertia of the door and decelerates the door, but it does not move easily even if the door is opened with great force. Even if the resistance Rj3 acting on the door closer is small, the force to decelerate the door is large.

The force that opens the fully closed door is a force that acts on the door when the door is fully closed. The stronger the pull spring V presses the door, the greater the force that opens the fully closed door. A door closer equipped with a normal hydraulic cylinder with a built-in strong spring that overcomes the viscous resistance of oil and rotates the door is fully closed when both the rotating body J and link A are substantially perpendicular to the fully closed door surface. Will not move even if I try to open the door.
Patent Document 1 The door is characterized in that the force of the spring that biases the door is small. In FIG. 1C, even when the axial center line Zj of the rotating body J and the line of action of the full closing force Fb are substantially in a straight line when fully closed, the door closer moves with a small force. A large force acts on the door to move the door. This means that even if the door moves with a large force, the door closer can counteract with a small force, and the door of Patent Document 1 opens the fully closed door unless the spring force that biases the door is small. Absent.

In the door of Patent Document 1, the rotation of the rotating body J is small in the range (A), and the speed reduction means Rj1 operates almost only in the range (I). The door of Patent Document 1 is designed to delay the movement of the rotating body J (door closer) within the range of (Yes) so that the door inertia force acts as a large braking force as it is. Resistance due to the door inertia force is If the door stops, it disappears, and the stopped door can be rotated without resistance.
The magnitude of the force Fd acting on the door is reduced by the magnitude of the resistance acting on the rotating body J, and there is no force to turn the door. When the door stops, if it is slowed down using frictional resistance, the resistance will continue to be applied after stopping, so the door will not move again, but deceleration due to the viscous resistance of fluid such as air or oil If the door inertia force increases, it automatically increases and decelerates the door.If the door stops, the flow stops and there is no resistance, and the biased door stops. Start moving without leaving.
The deceleration due to the resistance due to the inertia force of the door and the viscous resistance of the fluid such as air or oil is lost when the door stops, and the stopped door can be rotated without resistance.

In the link device in which the rotating body J rotates greatly in the range of (ii) like the door closer of Patent Document 1, the rotating body J can be used even if the resistance force is small as in the speed reduction means Rj1 shown in FIG. It resists rotation in the direction of arrow A in the figure and can accept a large door inertia force on the sliding surface KK. The decelerating means Rj1 is substantially independent of the door and does not resist the door, and the cylinder leaks air. Cylinders that can withstand air pressure do not have to be made rugged and the device is smaller. This is the feature of the door of Patent Document 1.

The door of Patent Document 1 is in the range of (Yes), and the force of the tension spring V rotates only the rotating body J without rotating the door. If the speed reducing means Rj1 and Rj2 are not attached to the rotating body J shown in FIG. 1, the force of the pulling spring V causes the rotating body J to rotate faster even if it is large, further accelerating the door.
The decelerating means Rj1 and Rj2 are for reliably reproducing the air resistance acting on the door surface, and the decelerating means Rj1 decelerates the door before the latch contact, and the decelerating means Rj2 decelerates thereafter.

If the deceleration is performed only after the latch contact, the door will be decelerated abruptly with little rotation, and an impact close to a collision will act on the door. When the door collides with the door stop when fully closed, the impact is received at a position farther from the pivot O, but when it stops suddenly just before the full closure, the impact is received at the door closer mounting portion near the pivot O. The inertial force proportional to the door weight is expanded by the lever principle, and the mounting bolts of the door and the door closer are pulled out.
For this reason, it is necessary to decelerate by the decelerating means Rj1 within a large rotation range of the door before the latch contact, and it is desirable that the door temporarily stops after the latch contact and starts rotating again to be fully closed. .

Even if the door stops and is fully closed, it is inevitable that the impact sound will be harsh if it accelerates within the range of (i). The decelerating means Rj2 is provided to soften the impact sound as much as possible, and is for fully closing the door that has started to rotate again with the door sufficiently decelerated at the time of latch contact.
The container Sp is an elastic body, and is made of an elastic film made of natural or synthetic rubber that expands and contracts greatly due to a slight pressure difference between the inside of the container Sp and the outside of the container Sp, and expands or contracts the volume. The volume of the gas or liquid to be filled is restored to a constant level. Further, the container Sp is a spoid provided with an inlet / outlet S1 that ejects the fluid contained in the container Sp or sucks the fluid outside the container Sp.
Even if the container Sp contracts and the air Fl filled inside the container Sp passes through a small hole entrance / exit S1 and is discharged to the outside of the container Sp, the container Sp is expanded by an elastic force and restored to the original shape before the contraction. The same amount of air as the discharged air is sucked in, and the container Sp maintains a constant capacity. A container Sp having a bellows shape is shown in FIG.

As shown in FIG. 1B, when the spoid container Sp abuts on the plate Pl provided on the door frame W, the entrance / exit Sl of the spoid container Sp is brought into close contact with the plate Pl, and the air filled inside the spoid container Sp. Fl gradually leaks out of the spoid container Sp through the entrance / exit Sl. The greater the amount of air Fl discharged per unit time, the greater the resistance to the air Fl discharge, and the greater the pressure difference between the inside and outside of the spoid container Sp, the greater the door speed.
When the door is decelerated and the speed becomes zero and the air Fl is not discharged, only the force that the spoid container Sp expands and restores acts on the door. The force for expanding and restoring the spoid container Sp is much smaller than the force resisting the door as the air Fl is discharged. When the air Fl is not discharged, the speed reducing means Rj2 almost resists the door. Without closing the door, the force Fd acting on the door is hardly reduced.
As shown in FIG. 1B, when the fluid is air, it is not necessary to return the air discharged from the spoid container Sp into the spoid container Sp, but liquid such as oil is a fluid discharged from the spoid container Sp. If all of the above does not return to the spoid container Sp, the fluid in the spoid container Sp will gradually disappear. It is necessary to return and accommodate all of the discharged fluid.

The speed reduction means Rj3 shown in FIG. 2 is prepared by preparing the two spoid containers Sp shown in FIG. Are provided with fluid inlets / outlets S11, Sl2, respectively, so that the inlets / outlets S11, S12 are brought into close contact with each other to form a common inlet / outlet Sl, so that the fluid entering / leaving through the common outlet / sl does not leak out of the two containers Sp1, Sp2. It is what you want to do.
An external pressure acts on one of the two containers Sp1 and Sp2, and a pressure difference of the fluid contained in each of the spoid containers Sp is generated. The time until the external pressure and the internal pressure of the fluid enclosed in the spoid container Sp are balanced is delayed. When the external pressure is removed, the pressure difference is reversed, the pressure difference disappears, and both of the two containers Sp1 and Sp2 are restored to return to the original volume.

An elastic body in which the capacity of one container Sp1 and the other container Sp2 is restored and the capacity returns to the original, and the fluid discharged by contracting one container Sp1 as the rotating body J rotates in the direction indicated by the arrow B Fl is accommodated while the other container Sp2 is inflated, and resists rotation of the rotating body J in the direction of arrow A in the figure. If the rotating body J is decelerated and stops, the flow of the fluid through the common entrance / exit Sl stops and resistance is lost. The rotating body J that continues to be energized even if it stops stops rotating again.
As shown in FIG. 2 (b), when the door D is rotated while the one container Sp1 is contracted, in addition to the force necessary for rotating the door, an extra force is required for the one container Sp1 to contract. is necessary. The force for contracting one container Sp1 becomes resistance, and the stationary door does not start to rotate again.

The force Fd acting on the door in the range of (ii) is a force that is large enough to move the door even if the latch male part Rd abuts the latch female part Rw and the door is stationary. This is a force (hereinafter referred to as a full closing force) of a magnitude that causes the male part of the latch to be recessed inside the door to fully close the door.
FIG. 2 (b) is a state diagram when the rotating body J contracts the container Sp1 in the range of (Yes), and when the force Fd acting on the door is largely switched and then becomes a full closing force. It is a state diagram. Prior to the latch contact, the force for contracting one of the containers Sp1 is equal to or less than the full closing force, and the door is not accelerated and stopped.
In FIG. 2 (b), when the container Sp1 contracts is at the time of latch contact, and the force for biasing the door by the spring V is not more than the full closing force, the latch is recessed when the door is stopped. The door cannot be fully closed.

The same applies to FIG. 1B, and after the door is decelerated, the wheel B returns to the sliding surface K. At this time, when the door stops at the time of latch contact, the resistance of the decelerating means Rj1, Rj2 If a resistance other than the above acts, the door remains stationary when the force Fd acting on the door is a full closing force.
If the force Fd acting on the door is made to force the door to fully close while the container Sp1 is contracted while the container Sp1 is contracted, not only will the speed of contracting the container Sp1 increase but the range Sp However, the force Fd acting on the door increases, and the acceleration of the door in the range (A) increases.
If the force Fd acting on the door is made larger than the full closing force and the stationary door starts to move, the door will accelerate in both the range (A) and the range (I). If the resistance is further increased and the speed is reduced, it may remain stopped.

The force Fd acting on the door is around the pivot axis O in order for the door to move regardless of the position where the hand is released from the door and the door starts to close with the restoring force of the spring (hereinafter referred to as the closing start position). It must be a force slightly larger than the maximum static frictional force acting on the rotation (hereinafter referred to as the minimum biasing force). A moving frictional force smaller than the maximum static frictional force acts on the moved door, and an excessive force is applied to rotate the door.
Also, when the moving door stops, the frictional resistance returns from the kinetic frictional force to the maximum static frictional force, and if it is not greater than the force that moves the moving door, the stopped door can be moved again. Absent.

If a door that rotates with a force slightly exceeding the maximum static friction force is resisted to decelerate, or if further resistance is applied, such as a force that contracts the container Sp1, the door will stop again if the door stops. Does not move. Doors that rotate with a force slightly greater than the maximum static friction force are further accelerated.
Attempts to reduce the acceleration by applying frictional resistance to the moving door will remain stopped if the door stops, and it will automatically occur and disappear automatically like air resistance acting on the door surface. If it doesn't, you can't slow down without leaving the door stopped.

Even if air resistance is adopted as the speed reduction means, there is a considerable frictional resistance, and the force Fd acting on the door must be increased to overcome the frictional resistance and rotate the door. When friction resistance that acts more strongly after deceleration is adopted for the deceleration means, it is difficult to adjust the force that biases the door, and if the biasing force is increased too much so that the friction resistance is not overcome and stopped Then, the door is fully closed without decelerating. If the urging force is insufficient, the door stops and cannot be fully closed.
When the speed reducer operates even if air resistance is used, more or less frictional force works, and when rotating the door while operating the speed reducer, an extra force other than rotating the door is required. In order to decelerate the accelerated door, a vicious cycle occurs in which the force that the decelerator operates further increases.

The door of Patent Document 1 does not increase the force Fd acting on the door more than necessary, and minimizes the acceleration of the door, and minimizes the strain energy of the spring that rotates the door to minimize the acceleration. It only suppresses the effect of the air resistance that acts on the door surface and disappears naturally. Even if the speed reduction means is applied, the result is that the door is accelerated.
It is not only possible to remove the acceleration in the range (A) by adjusting the magnitude relationship of the force, but also the force Fd acting on the door in the range (A) suddenly increases and the door suddenly Accelerates and does not prevent a violent impact sound when it is fully closed.

It is easy to decelerate, and if you decelerate without spending time, it becomes a collision. The impact sound is converted into sound when the door speed instantaneously becomes zero and the kinetic energy of the door becomes zero in a very short time. If the kinetic energy of the door is consumed over a long time due to frictional loss of resistance, the door speed becomes zero after a long time and is not converted into sound.
The problem is how to decelerate slowly by consuming the kinetic energy of the door just before it is fully closed over a small range of rotation of the door in the range of (い) over time.

The reason why the door of Patent Literature 1 is fully closed is that air resistance greatly contributes to the deceleration of the door. A flow is generated in the air between the door surface and the door frame, and the rotation of the door is resisted by the disturbance of the flow. The resistance becomes more prominent as it approaches the fully closed position, and the impact sound is reduced. However, the opening and closing of the door causes air to enter and exit between the door surface and the door frame because of a pressure difference between the inside and outside of the room. The door in the room where the window is closed slows down, but the window opens. The room door has less deceleration. The door of Patent Document 1 must be decelerated and fully closed in the same manner as in the case of receiving the air resistance, whether the window is opened or a gust of wind blows on the door.

The force when the door stops and the latch is recessed to fully close the door is large, and the force when the door does not stop and the latch is recessed and the door is fully closed is too small to compare. If it does not matter that the latch is stopped while contacting the door frame W after the door Sp1 is decelerated while the container Sp1 is contracted, the force that biases the door with the spring V is far greater than the full closing force. The force when opening a fully-closed door that becomes smaller is extremely small.
The door of Patent Document 1 continues to accelerate in the range (A) and further accelerates in the range (I), and expects the effect of air resistance acting on the door surface. If the spring force is not minimized as long as it can be stopped halfway, a large force will not be required to open the door, and it will be slowed down so that it will not emit a violent impact sound when fully closed. I can't.

1 and 2 show that the rotating body J stops when the door stops, but FIG. 3 shows a link device in which the rotating body J can move greatly even when the door stops in the switching range. Since the force Fd acting on the door changes greatly after the rotating body J moves greatly, the door is decelerated while the rotating body J is moving greatly, and even if the door stops, it does not remain stopped. Is.
In FIG. 3, the tension spring V fixes and supports one attachment portion on a fixed support shaft Sw provided on the door frame W, and movably supports the other attachment portion on a support shaft Pv provided on the rotating body J. The rotating body J is rotatably supported around a connection axis C provided on the door D, and rotation in the direction opposite to the arrow A in the figure is prevented by a contact Gj provided on the door D.

3 (a1) and 3 (b1) are state diagrams in the range (A). The axial center line Zv of the tension spring V is closer to the door surface than the connecting shaft C, and the rotating body J is hit from Gj. Does not rotate and does not rotate. As the tension spring V expands and contracts, the door D rotates in the direction of arrow B in the figure. FIGS. 3 (a2) and 3 (b2) are state diagrams of the switching range. When the axial center line Zv of the tension spring V crosses the connection axis C, the rotating body J moves away from the contact Gj, and the connection axis Rotate in the direction of arrow B in the figure around C.
FIGS. 3 (a3) and 3 (b3) are state diagrams in the range of (Yes), and the rotating body J rotates greatly to increase the distance Lv between the axial line Zv of the tension spring V and the pivot O. A large force acts on the door, and the door is fully closed.

Since the rotating body J moves independently of the door in the switching range, no matter how large the resistance is set to decelerate the door, as long as the rotating body J continues to rotate with a force that exceeds the resistance, How does the door stay stuck?
As shown in FIG. 3A, the distance Lv between the line of action of the force of the spring V of the biasing means and the pivot O is set to zero within the range (A), and the spring V of the biasing means is If the biasing means Vd in the range (A) is provided separately from the biasing means V in the range (B), as shown in FIG. Even if the door is decelerated with a large frictional resistance in the range (ii) and the force for energizing the door is increased to overcome the frictional resistance, the door is not energized in the range (a).

In addition, the reduction gears Rj1 and Rj2 shown in FIG. 1 and FIG. 2 are interlocked with the rotating body J and move slightly in the range (A), move greatly in the range (I), overcome the frictional resistance, and rotate the rotating body J. The force that rotates the wheel causes further acceleration of the door both in the range (ii) and in the range (a), and a greater resistance must be applied. In FIG. It does not rotate at all in the range of a) and only rotates after the switching range. Even if resistance is applied to the rotating body J, the resistance works only after the switching range. The force for rotating the rotating body J works only after the switching range, and does not reach the range (A) no matter how much the force working after the switching range is greater than the full closing force. Even if the vehicle is accelerated after the switching range, the door is not further accelerated in the range (A), and no additional resistance is required in the range (A).

If the switching range does not end instantaneously but progresses slowly over time, the resistance works and slows down the door. Even if a large resistance is applied to the door D so as to stop the door, the rotating body J rotates regardless of the force Fd acting on the door from small to large.
Even if the resistance is removed after switching, or even if the resistance cannot be removed, the door does not stop or the door stops by switching the force Fd acting on the door to a force greater than the full closing force. You can start moving again. The force for decelerating the door and the force for energizing the door can be adjusted separately to facilitate the operation.

The spring that rotates the rotating body J is a spring that rotates the door, and both the speed reduction device Rj1 and the speed reducing sliding surface KK are resistances acting on the rotating body J in the switching range. When the axial center line Zv of the spring crosses the connection axis C, the force for urging the rotating body J is weak, and if the resistance is smaller than the resistance acting on the rotating body J, the door D rotates with the rotating body J stopped.
The reduction gear Rj1 does not function, and the reduction sliding surface KK stops the door D. If the resistance acting on the speed reducer Rj1 and the rotating body J of the speed reducing sliding surface KK is large, the rotating body J remains stopped, and if it is small, the rotation of the rotating body J ends instantaneously.
Only when the rotating body J starts to turn to the end in the switching range, the force for decelerating the door and the force for energizing the door can be adjusted separately, but the force for decelerating the rotating body J It is not easy to separately adjust the force for urging the rotating body J.

The distance Lv between the line of action of the force of the spring V of the biasing means and the pivot O is set to zero in the range (A), and the biasing means Vd in the range (A) is set in the range (A). If not provided separately from the force means V,
Since the spring that operates the speed reducer is also the spring that rotates the door, the force of the spring is increased by an amount that overcomes the resistance of the speed reducer. It is necessary to increase the resistance of the speed reducer by accelerating the door as much as it increases. Increasing the resistance further accelerates the door, making it difficult to adjust the speed reducer and spring.
In FIG. 3 (b1 to b3), the spring for rotating the rotating body J and the spring for rotating the door are separate, and rotate within the switching range with little influence on the magnitude of the resistance acting on the rotating body J. The body J can be rotated. Neither the rotating body J nor the door D remain stopped.

In the door closer of FIG. 3 (b1 to b3), a spring for rotating the door and a spring for operating the speed reducer are provided separately, and the spring for rotating the door rotates the door without operating the speed reducer. A spring that activates the decelerator operates without rotating the door.
Friction resistance can also be adopted for the speed reducer, and even if the friction resistance is increased and the spring for operating the speed reducer is increased to greatly decelerate the door, the function of energizing the door is not affected. Since the spring for rotating the door and the spring for operating the speed reducer do not affect each other, they can be easily adjusted separately.

The door closer shown in FIG. 3 (b1 to b3) is urged by a spring that is rotated by a spring that starts moving wherever it stops, and the resistance automatically acts on the door at a predetermined opening degree of the door. However, even if the resistance acting on the door disappears automatically, and the door stops due to the resistance, the spring that rotates the door rotates the door when the resistance disappears automatically. The door will not stay stationary.
Even if the resistance adopted for the speed reducer is not a resistance that automatically occurs and disappears automatically like "Air resistance acting on the door surface", the speed reducer starts to move and does not stop until the end. If so, the resistance employed in the reduction gear may be a frictional resistance that continues to work even after acting, such as the resistance of a brake shoe or gear mechanism. Further, such a deceleration means can decelerate the door without decelerating at any opening degree of the door, even if the range of decelerating the door is not limited to the range (ii).

In FIG. 3 (b1 to b3), the rotating body J and the rotating body JJ have a common rotating shaft, and the rotating body J is provided with a contact G1 and a contact G2, and the rotating body JJ has a position where the contact G1 contacts and a contact G2. Swing between the contact position. The link AA is connected to the rotating body JJ, and the wheel B is mounted on the wheel support shaft Ib provided at the tip of the link AA. Due to the rotation of the rotating body JJ, the wheel support shaft Ib moves along the groove M and swings between the start end portion Ms and the end end portion Me of the groove M. The movement of the wheel spindle Ib along the groove M is decelerated by the decelerating means Rj2 shown in FIG.

When the fully closed door is opened, the rotating body JJ rotates in the same direction as the rotating body J while abutting against the G1 as the rotating body J rotates in the direction opposite to the arrow A in the drawing. The spring VV that urges the rotation of the rotating body JJ is a toggle spring, and is provided separately from the spring V that urges the door. When the axial center line Zvv of the tension spring VV crosses the connecting shaft C, the rotating body JJ rotates away from G1, the wheel support shaft Ib contacts the starting end Ms, and the rotation of the rotating body JJ stops.
As shown in FIG. 3 (b1), in the process of closing the door, even if the axis Jv of the tension spring V crosses the connecting axis C and the rotating body J starts to rotate in the direction of the arrow a in FIG. Remains stopped, the wheel spindle Ib remains at the start end Ms, and the spoid container Sp does not contract.

As shown in FIG. 3 (b2), when the axial center line Zv of the tension spring V crosses the connecting axis C, the rotating body J hits and starts rotating away from Gj. The rotating body JJ does not rotate until the contact G2 contacts the rotating body JJ, and as shown in FIG. 3 (b3), the contacting G2 contacts the rotating body JJ and the rotating body JJ rotates before the latch contact. Begin to.
As shown in FIG. 3 (a2), instead of starting to contract the spoid container Sp at the same time that the axial center line Zv of the tension spring V crosses the connecting axis C, as shown in FIG. After a large rotation, the force of the pulling spring V acts on the rotating body J so that the force of the pulling spring V can sufficiently contract the spoid container Sp, and the contact G2 comes into contact with the rotating body JJ to rotate the rotating body. JJ begins to rotate.

If the resistance acting on the speed reducing device Rj1 and the rotating body J of the speed reducing sliding surface KK is large, the rotating body JJ remains stopped, and if it is small, the rotation of the rotating body JJ does not end instantaneously. After the axis Zvv of the tension spring VV crosses the connection axis C, the rotating body JJ is urged by the tension spring VV and rotates.
The wheel support shaft Ib moves away from the starting end Ms, and the spoid container Sp begins to contract. The rotating body JJ rotates slowly until the wheel spindle Ib reaches the terminal end Me, and the rotating body J rotates relatively integrally with the rotating body JJ. The rotating body JJ decelerates the rotating body J while coming into contact with G2.

The link device shown in FIG. 1 and FIG. 2 is a structure in which if the door closer moves slowly, if the door is rotated in the closing direction, the door closer resists this even if the door moves rapidly in the closing direction. The body J rotates even with a small force, and is difficult to turn even if it tries to move with a large door inertia force. The door closer shown in FIG. 3 has a structure in which, if there is no deceleration sliding surface KK, the rotating body J continues to move even if the door stops after the switching range, and the door closer and the door do not interlock. In this case, the rotating body J moves regardless of whether the door moves or not, and the door closer does not resist the door inertia force.
As shown in FIG. 3, when the speed reducing sliding surface KK is provided on the door frame W and the wheel B moves slowly along the speed reducing sliding surface KK, the rotational speed of the door is reduced. Follow the speed of wheel B moving along KK. Further, even when the link device is not “a structure capable of rotating with a small force and resisting a large door inertia force” as in the link device of FIGS. The groove M supports the large door inertia force and resists the large door inertia force.

When the wheel B moves in the direction of arrow C in the figure along the speed reducing sliding surface KK, the rotating body J or the rotating body JJ rotates in the direction of arrow A in the figure. The gradient of the deceleration sliding surface KK mitigates the impact when the wheel B collides with the deceleration sliding surface KK.
The door inertia force is a force with which the wheel B presses the deceleration sliding surface KK, and the force Fk with which the deceleration sliding surface KK pushes back the wheel B decelerates the door. When the door decelerates and the door inertia force decreases, the pushing force Fk also decreases. When the door stops and the door inertia force disappears, the pushing force Fk disappears. The door inertia force is the same magnitude, works in the opposite direction, and is converted into a force that slows down the door.

In FIG. 3B, the wheel B moves along the sliding surface KK, but the same effect is obtained even when the wheel B is fixed to the door D and the sliding surface KK moves along the wheel B. Is obtained. In either case, the sliding surface KK moves relative to the door D in a direction substantially perpendicular to the direction of movement of the door D. The door inertia force that supports the large door inertia force and continues to move with a small force is the wheel B. The action line of the pressing force Fk approaches the radial direction of the circular motion of the wheel B as the door approaches the fully closed position, and the sliding surface KK supports a large door inertia force. . The sliding surface KK continues to move with a small force by moving in the circumferential direction.

The speed reducing sliding surface KK is a full closing prevention means for preventing the door from being fully closed without being sufficiently decelerated. As shown in FIG. 3 (a2), the pressing force Fk received by the wheel support shaft Ib is , Supported by the rotation axis C of the rotating body J. By reducing the distance between the line of action of the pressing force Fk and the rotation axis C of the rotating body J, the rotating body J can rotate with a small force while supporting a large door inertia force. If the distance is large, the rotating body J easily rotates by a large door inertia force, does not support the door inertia force, and does not decelerate the door.
In FIG. 3 (b1 to b3), the rotation of the rotating body JJ is converted into a reciprocating motion along the groove M in which the wheel support shaft Ib is substantially parallel to the door surface via a link AA. Is substantially at right angles to the groove M, and the groove M can support a large door inertia force while hardly resisting the movement of the wheel B.

The door D in FIG. 3 is in contact with the sliding surface KK through the wheel B at the contact point b. The contact b moves greatly in the direction perpendicular to the movement direction while moving slightly in the movement direction of the wheel B. In FIG. 3, the sliding surface KK is substantially perpendicular to the movement direction and is fixed to the door frame W. The wheel B moves along the sliding surface KK while moving along the groove M provided in the door D, but the wheel B is fixed to the door D and the sliding surface KK moves along the wheel B. However, the same effect can be obtained. In this case, the contact point b between the door D and the sliding surface KK moves slightly in the movement direction, while the sliding surface KK moves greatly in the direction perpendicular to the movement direction.
The effect is the same if the sliding surface KK, which is slightly inclined in the direction perpendicular to the direction of movement of the wheel B, moves relatively in the direction perpendicular to the direction of movement of the wheel B. The sliding surface KK is a hit for preventing the movement of the wheel B, and the hit G is retracted. The sliding surface KK is a means for preventing movement of the wheel B that slowly moves backward.

As shown in FIG. 3 (a3), when fully closed, the wheel B moves along the sliding surface K, and the door is fully closed only by the force of the tension spring V. As in FIG. 1C, in the door, the wheel B is separated from the deceleration sliding surface KK and does not resist the rotation of the door. The device of FIG. 3 is a link device that continues to move even if the door stops, and automatically releases the resistance that slows down the door D.
As shown in FIG. 3 (b3), when fully closed, the wheel B moves away from the deceleration sliding surface KK and does not resist the rotation of the door. The door rotates only with the force of the pull spring V.
Just as the air resistance acting on the door surface disappears immediately before full closing and the door is fully closed, the resistance acting on the door disappears immediately before full closing and the door is fully closed.

FIG. 4 is an explanatory diagram of the link device shown in FIGS. The door D is rotatably supported around a pivot O provided on the door frame W, and the distance between the connection shaft C provided on the door D and the fixed support shaft Sw provided on the door frame W changes. Rotate. The door D is a link having two connecting shafts of a pivot axis O and a connecting shaft C at both ends, and the door frame W is a link having two connecting shafts of a pivot shaft O and a fixed support shaft Sw at both ends. The door frame W shares the pivot O and opens and closes around the pivot O. A portion composed of the door D and the door frame W is an opening / closing portion, and a portion between the connection shaft C and the fixed support shaft Sw is an expansion / contraction portion. The door closer is a device that is incorporated in an expansion / contraction section and rotates the door D in the closing direction by the restoring force of the spring that rotates and expands / contracts the door D in the opening direction.

The opening / closing part and the expansion / contraction part constitute a link device, and the simplest structure of the link device for rotating the door D is rotatable around the connection axis C as shown in FIG. 4A and illustrated in FIG. A structure in which a slider B is mounted on a rotating body J that is pivotally supported by the shaft and moved along a sliding surface K provided on the door frame W, or as shown in FIG. 2B and illustrated in FIG. A structure of a four-bar rotation mechanism in which a connecting shaft P and a fixed support shaft Sw provided on the body J are connected by a link A, or a structure in which the expansion and contraction portion is a spring V as shown in FIG. The spring V replaces the two links shown in FIG. 4 (b), and FIG. 4 (c) is a link device constituted by links that expand and contract instead of rigid links. The link device of the present invention is limited to the three shown in FIGS. 4 (a), 4 (b), and 4 (c).

In each of the two link devices shown in FIGS. 4 (a) and 4 (b), when the door D does not rotate, the sliding surface K is centered on the connecting shaft C as shown in FIG. 4 (d). When the wheel R follows the circular motion of the wheel B, or as shown in FIG. 4E, the rotating body J and the link A are infinitely long and the connecting shaft C is fixed to the fixed support shaft Sw. When the rotating body J and the link A overlap and operate as one link, or when the rotating body J and the link A are infinitely short as shown in FIG. If the rotating body J is as short as possible, the link A can rotate greatly, but the link device approximates a triangle composed of the door D, the door frame W, and the rotating body J and cannot move.

In the process in which the door D is closed, the rotating body J rotates more greatly while the door D slightly rotates as the link device approaches the state shown in FIGS. 4 (d) to 4 (f). In particular, when the axial center line Zj of the rotating body J is in the circumferential direction of a circle around the pivot axis O, the rotating body J rotates with a small force, and a large force acts on the door D. At the same time, even if a large force acts on the door D and rotates, a small force acts on the rotating body J to resist the door D.
The door D has a weight, and the inertia force acts on the door D in addition to the force of the spring V. A large force is required when the door D starts to move and when it tries to stop the rotating door D. Immediately before the door is fully closed, the closer to the state where the rotating body J intersects the door D surface at a right angle, the rotating body J fully closes the door D with a large force while supporting a large door inertia force.

As the link device approaches the state shown in FIG. 4D to FIG. 4F, the door accelerated immediately before closing causes the door closer to rotate at a high speed, and the rotating body J rotates with almost no load. And finish. By merely rotating the rotating body J slowly, the rotating body J can decelerate the door while supporting the large door inertia force while rotating with a small force. As the door decelerates, the door inertia force decreases.
The door stops, the inertial force of the door becomes zero, and the rotating body J rotates with a small force while the large force acts on the door to fully close the door. In order to decelerate the door, it is not necessary to increase the force for rotating the rotating body J, and the door can be sufficiently decelerated by the force for fully closing the door.
The present invention mainly relates to a means for slowly rotating the rotating body J in the special state shown in FIGS. 4 (d), 4 (e), and 4 (f).

In the present invention, the door is decelerated when the rotation of the door is small and the rotating body J is large, so that even if the door stops, a large force is applied so that the door starts moving again, or the door is stopped. Even the door closer needs to keep moving.
As for the two link devices shown in FIGS. 4 (a) and 4 (b), the link device in which the door closer continues to move even if the door stops is shown in FIG. 4 (g) and illustrated in FIG. A device that replaces one of the links with a spring, or replaces one of the links with two links as shown in FIG. 4 (h) (for example, link A in FIG. 4 (b) is replaced with link A and link AA). As shown in FIG. 4 (i), one of the connecting shafts of the surrounding pair is replaced with a sliding pair.

In any case, when the door D and the door frame W of the link device shown in FIGS. 4 (g), 4 (h), and 4 (i) are regarded as one link, FIG. 4 (a). 4 (b) and 4 (c), and can be exercised. 4 (g), FIG. 4 (h), and FIG. 4 (i), the door D and the door frame W can be regarded as one link because the rotation around the pivot axis O is eliminated. is there. Similarly, even if the connecting shaft that does not rotate is a connecting shaft other than the pivot O, it can move.

When the link device increases the degree of freedom, for example, by increasing the number of links, two or more motion forms are possible. The link device of FIG. 3 is a link device in which one link is added to the link device shown in FIG. 4 (c), and the added link is urged by a toggle spring and swings between two stationary positions. Two modes of motion are possible.
In FIG. 22, the link device with an increased degree of freedom has different movements when the link device moves and stops, and the door is fully closed in a state in which the restoration of the spring expanded and contracted by the door inertia force is stopped.

The door closer includes a rotating device that rotates the door within the range (A) and a fully closing device that fully closes the door while decelerating the door within the range (I). FIG. 5 is a device that operates only from the time when it is fully closed to the time when it is fully closed.
The wheel B attached to the door D (not shown) moves in the direction of the arrow B in the figure along the track Zb, abuts against the sliding surface K provided on the single gear Jk, and the single gear Jk around the fixed support shaft Sww. Rotate in the direction of arrow a in the figure.

The wheel B that moves in the direction indicated by the arrow B in the drawing along the track Zb and the single gear Jk that rotates in the direction indicated by the arrow B in the drawing relatively move together in the same direction.
When two objects that move in the same direction and have different speeds collide and move relatively together in the same direction, one of the two objects moving at a high speed is decelerated to the other moving at a low speed. Hereinafter, one moving at a high speed before becoming relatively united is called a moving body, and the other moving at a low speed is called a moving body.

The springs Va, Vb, and Vc for energizing the devices shown in FIGS. 5A, 5B, and 5C are all incorporated in the speed reduction means Rj1 shown in FIG. It expands and contracts slowly. (The speed reducing means Rj1 is not shown in FIGS. 5B and 5C.) Although the strengths of the springs Va, Vb, and Vc are different from each other, the rotation of the single gear Jk is decelerated to the spring and the door. If there is a force that decelerates, it is considered that there is a force to rotate the single gear Jk to fully close the door.

FIGS. 5 (a1), 5 (b1), and 5 (c1) are state diagrams before the wheel B comes into contact with the sliding surface K, and the single gear Jk hits and presses Gw to stand by. FIGS. 5 (a2), 5 (b2), and 5 (c2) are state diagrams after the wheel B contacts the sliding surface K, and the springs Va, Vb, and Vc urge the single gear Jk. The direction is reversed from the direction that hits Gw, and the single gear Jk rotates in the direction of arrow A in the figure. The wheel B and the single gear Jk move relatively integrally, and the rotational speed of the door D follows the rotational speed of the single gear Jk. As the springs Va, Vb, Vc slowly expand and contract, the sliding surface K of the single gear Jk decelerates the door D, and the sliding surface KK fully closes the door D.

Since the rotation of the single gear Jk is directly transmitted to the expansion and contraction of the spring Va in the apparatus of FIG. 5A, the speed reduction means Rj1 of the apparatus of FIG. 5A is comparable to the assumed magnitude of the door inertia force. It is necessary to have resistance. Since the resistance force is large, the device becomes a high-pressure vessel, and a strong spring exceeding the resistance force is built in, so that the total closing force becomes excessively large.

The rotating body J of the apparatus of FIGS. 5B and 5C supports most of the door inertia force as in the rotating body J shown in FIGS. 1 and 2, and the springs Vb and Vc The rotating body J is rotated with a small force.
The speed reduction means Rj1 of the apparatus shown in FIGS. 5B and 5C only needs to resist a force much smaller than the assumed door inertia force. The device does not need to withstand high pressure, does not need to contain a strong spring, and the total closing force is reduced. Therefore, the force when opening a fully closed door is small.

5 (b) and 5 (c), the rotating body J is rotatably supported around Sw. In FIGS. 5 (b2) and 5 (c2), the direction of action of the rotational force of the single gear Jk. The rigid rotating body J resists the rotation of the single gear Jk.
In FIG. 5B, the wheel BB attached to the wheel spindle Ib provided at the tip of the rotating body J moves along the sliding surface Kb and the sliding surface KKb provided on the single gear Jk, and slides. The action line of the force Fb at which the moving surface Kb or the sliding surface KKb presses the wheel B is in the direction of the axis Zj of the rotating body J in FIG.

In FIG. 5 (c), the link A connects the connecting shaft C provided on the single gear Jk and the connecting shaft P provided on the rotating body J. In FIG. 5 (c2), the axis A Za of the link A rotates. This is the direction of the axis Zj of the body J.
5 (b2) and FIG. 5 (c2), the state in which the axial center line Zj direction of the rotating body J is directed to the direction of the rotational force of the single gear Jk is maintained in the substantially entire rotation range of the single gear Jk. To do.
The door closer resists door rotation and is not easily turned by the door. Even if the rotational resistance around the fixed support shaft Sww is increased so as to resist further, the magnitude of the force Fd acting on the door does not exceed the full closing force and can be left as it is.

On the other hand, the fully-closed device in FIG. 5A is a fully-closed device and does not have a function of resisting the rotation of the door, and has a structure that is easily turned by the door. A normal door closer is a device that rotates a door in a wide range including the range (A), and the fully-closed device in FIG. 5A is a device that rotates the door in the range of the range (A). There is only the same structure and function and does not support the large door inertia force. If the spring force is not increased as much as the rotational resistance around the fixed support shaft Sww is increased, the spring will remain stopped, and the force for fully closing the door will also increase, so the speed will not be reduced unless the resistance is further increased.

The fully closing device in FIG. 5 (a) finally closes the door, but continues to support the inertial force of the door in the entire operating range before the fully closing and functions to resist the rotation of the door. Is mainly provided. In the fully closing device of FIG. 5 (a), the axial center line Zjk direction of the single gear Jk is substantially perpendicular to the direction Fb in which the door inertia force acts, but the fully closing device of FIGS. 5 (b) and 5 (c). As described with reference to FIGS. 1 and 2, the axial direction Z of the link is the circumferential direction of the circular motion of the single gear Jk.

The single gear Jk in FIGS. 5 (b) and 5 (c) decelerates the progress of the wheel B while the means for preventing the progress of the wheel B is retracted, and prevents the door from rotating in the closing direction. The contact is a slow movement in the direction of travel of the door, and is hereinafter referred to as a rotation prevention means that moves backward.
The wheel B does not move by the force that urges the door, but the wheel B stops in a direction different from the force that urges the door in the direction that the wheel B moves by the force that urges the door. I try to move.
Since the door is energized by the force that starts moving wherever it stops, even if some resistance acts on the door and the door stops, the door starts to move when the resistance is removed. The reverse rotation preventing means may be any means that automatically releases the resistance that acts on the door and decelerates the door. Also, the door stops when the reverse rotation prevention means stops, so it must not stop halfway when it starts moving.

The reverse rotation prevention means moves slowly at the contact point with the door while being relatively integrated with the door. The moving direction of the contact point is substantially perpendicular to the direction of the action of the door inertia force, supports a large door inertia force, and can move with a small force. Even if the structure of the link device of the door closer does not include the “rotating body J that supports the large inertia of the door and rotates greatly with a small force” as shown in FIGS. By providing the means, the door closer becomes the same as the one provided with “the rotating body J that supports a large door inertia force and rotates largely with a small force”.
5 (b) and FIG. 5 (c) have the same structure as FIG. 1 and FIG. 2, respectively, and the single gear Jk of FIG. 5 (b) and FIG. 5 (b) and FIG. 5 (c) are the same as FIG. 1 and FIG. 2, respectively.

The door closer shown in FIG. 6A is moved by a spring different from the spring that biases the reverse rotation preventing means, but the door closer shown in FIG. 6B is prevented from rotating when the spring biasing the door moves backward. The means can be moved, and the door and the anti-rotation means that move backwards also move with the same spring.
The spring that biases the door has a force to start moving wherever the door stops, but does not have the force to operate the reverse rotation preventing means. The reverse rotation prevention means in FIG. 6 (a) automatically releases the resistance and the door does not remain stopped, but the door closer in FIG. 6 (b) has a spring that biases the door reverse. It switches to the force that also releases the resistance of the rotation prevention means, and remains stopped if the door stops before switching. If the door stops before the resistance is released, it stays stopped.

In the link device of FIG. 6, a rotating body J is pivotally supported around a connecting shaft C provided on a door D, a connecting shaft P provided on the rotating body J, and a fixed supporting shaft Sw provided on a door frame W. 4 is a link device described in FIG.
In FIG. 2, the rotating body J rotates greatly and a large force acts on the door when it approaches a state in which the axial center line Zj of the rotating body J and the axial center line Za of the link A approach each other. This is a time when the state approaches the state of being arranged on a line, and in FIG. 2 and FIG.

As shown in FIG. 1, the link device of Patent Document 1 that supports a large door inertia force and continues to move with a small force includes a rotating body J that is rotatably supported around a connection axis C provided on the door D. It is connected to the sliding surface K provided on the door frame W by a sliding pair, and a normal line standing on the sliding surface K passing through the contact point b between the rotating body J and the sliding surface K passes near the connection axis C. This is a link device in which the rotating body J rotates greatly.

Alternatively, as shown in FIGS. 2 and 6, a link A that is rotatably supported around a fixed support shaft Sw provided on the door frame W is connected to the rotary body J by a connecting shaft P and connected in pairs. This is a link device in which the rotating body J rotates greatly while maintaining a state in which the rotating body J and the link A overlap with each other or approximate to a state of being arranged on a straight line. The rotating body J supports a large door inertia force and continues to move with a small force. By simply applying a small resistance to the rotating body J and slowly rotating the rotating body J, the rotating door can be rotated slowly. .

1 "the normal line standing on the sliding surface K passing through the contact point b passes near the connection axis C" and "the rotating body J and the link A overlap each other or on a straight line shown in FIG. 2 and FIG. Is a state where the rotational force acting around the connecting axis C is transmitted to the door D via the contact b or the connecting shaft P, and “the force passing through the contact b or the connecting shaft P”. Rotation acting around the connection axis C when the force action line F moves away from the vicinity of the connection axis C. Force is not transmitted to door D.
When the contact b or the connecting shaft P moves in a direction substantially perpendicular to the “action line F of the force passing through the contact b or the connecting shaft P”, the rotating body J can rotate with a small force.

The link device in FIG. 6A is the link device described in FIG. 4H, and is a link device in which the link A is replaced with the link A and the rotating body JJ. The spring Vjj that urges the rotating body JJ is stronger than the spring Vj that urges the rotating body J, and as shown in FIG. The door D is rotated largely in the direction of the arrow B in the figure, while the rotating body J remains in contact with Gj.
As shown in FIG. 6 (a2), while the rotating body JJ is in contact with Gjj2 in the range of (ii), the rotating body J moves away from the winning Gj1 and rotates in the direction of arrow A in the figure. The movement of the link device in FIG. 6A differs between the range (A) and the range (I), and the rotating body J does not rotate at all within the range (A), but rotates greatly within the range (A). To do.
In FIG. 6 (b), the rotating body J rotates in the direction of arrow A in the figure, and rotates the door D in the direction of arrow B in the figure, but the length of the rotating body J is shorter than that of the link A. Thus, it rotates greatly in the range of (i).

The door closer shown in FIG. 6 also includes a rotation preventing means that moves backward, and the wheel B that is attached to the door D abuts against the sliding surface K that is attached to the door frame W, as in FIG.
In the case of FIG. 6A, the wheel B is mounted on the connecting shaft P, and the sliding surface K is attached to the single gear Jk that is rotatably supported around the fixed support shaft Sww provided on the door frame W. Similarly to the single gear Jk shown in FIG. 5 (b), the single gear Jk is in a standby state as shown in FIG. 6 (a1). The wheel B comes into contact with the sliding surface K provided on the single gear Jk, and the single gear Jk starts to rotate in the direction of the arrow C in the figure. The sliding surface K moves backward with respect to the traveling direction of the wheel B.

The rotation of the single gear Jk in the direction of the arrow C in the drawing is rotated by a spring that urges the single gear Jk regardless of the rotation of the door, and the door B stops because the wheel B presses the sliding surface K. However, the sliding surface K moves backward so that the wheel B can travel.
When the door and the door closer work together, if the door stays stopped, the door closer also stays stopped, but when the resistance acting on the door is naturally removed like air resistance, it starts moving again. Even when the door and the door closer are interlocked, if the reverse rotation preventing means is provided, as shown in FIG. .
The door closer structure shown in Fig. 4 is a link device that does not move easily even if a large force is applied to the door. Even if it acts, the door closer becomes difficult to move.
6 (a3) and 6 (b3) show a state in which the wheel B is separated from the sliding surface K and the resistance is released.

In both the case of FIG. 6A and the case of FIG. 6B, the rotation of the rotating body J does not continue unless the wheel B presses the sliding surface K to expand and contract the push spring U.
As shown in FIG. 6B, the pressing spring U biases the sliding surface K and hits Gk to stand by. When the wheel B moves along the groove M while moving along the sliding surface K, the push spring U is expanded and contracted. The wheel B cannot move unless a force is added to the force Fd acting on the door.

If the force that urges the rotating body J is increased so that the door remains stationary but does not remain stationary, the wheel B moves at a high speed, and the door accelerates without decelerating. The resistance due to the push spring U must be increased. If the resistance by the pressing spring U is increased, the force for biasing the rotating body J must be further increased.
When the door is decelerated in this way, if the door is rotated, the door will not move again if the door stops and resistance continues to work.

When the door and the door closer work together, the rotation of the rotating body J, the position of the wheel B in the groove M, and the amount of expansion and contraction of the push spring U by the wheel B pressing the sliding surface K are determined by the opening of the door. The expansion and contraction of the push spring U is interlocked with the rotation of the rotating body J, the amount of expansion and contraction is determined by the opening of the door, and the force for expanding and contracting the push spring U is also determined.
When the door rotates at a high speed and a large door inertia force works and the door rotates while the push spring U expands and contracts, the rotation amount of the rotating body J is less than the rotation amount uniquely determined by the opening of the door, and the push spring The expansion / contraction amount of U is also larger than the expansion / contraction amount uniquely determined by the opening of the door. If the force for rotating the door is insufficient while the push spring U expands and contracts, the door stops or decelerates.

In this case, the door inertia force is attenuated while expanding and contracting the push spring U, and the door is decelerated. At the same time, the restoring force of the push spring U causes the wheel B to move in the direction of the arrow C in the figure, and the door does not stop. .
As long as the wheel B moves along the groove M and there is sufficient force to press the sliding surface K and expand and contract the push spring U, even if the wheel B moves at a high speed, the deceleration means Rj1 The movement may be decelerated, and if the wheel B moves slowly along the sliding surface K, the door closes slowly.
The spring for urging the rotating body J is designed to urge the door strongly so as to cross the connecting shaft P when the push spring U is expanded and contracted. I try not to grow. While releasing the resistance in the range of (ii), the latch is recessed and the door is fully closed.

Fig. 7 (a) is a link device in which the door and the door closer are not interlocked as shown in Figs. 3 and 4 (g), and Fig. 7 (b) is the last. It is a link device that closes but does not interlock with the door and door closer until then. While the door and the door closer are not linked, the door closer can move even if the door stops, and even if the door closer moves slowly, it does not affect the rotation of the door.
The resistance Rg shown in FIG. 7 (a) is a frictional resistance acting around the pivot axis O.

Fig. 7 extends the time when the door and door closer are not interlocked, and decelerates the door with frictional resistance Rg while the door and door closer are not interlocked, so that even if the door stops, the force to release the frictional resistance Rg is increased. The door will not stay stuck. There is no means for releasing the frictional resistance after deceleration, such as the rotation prevention means for retreating, nor the fully closed prevention means for stopping the fully closed door without sufficiently decelerating.
If the rotating body J stops before starting to rotate, there is no force to release the frictional resistance Rg. Therefore, the rotating body J is rotating because the frictional resistance Rg acts after the rotating body J starts to rotate. Make the time as long as possible and decelerate the rotating door as much as possible.

A rotating body J is rotatably supported around a connection shaft C provided on the door D, and one attachment shaft of the tension spring V is fixedly supported on a fixed support shaft Sw provided on the door frame W, and the other attachment shaft is provided. Is movably supported on a connecting shaft Pv provided on the rotating body J. The rotation of the rotating body J in the direction opposite to the arrow A in the drawing is blocked by the contact Gj (not shown). FIG. 7 shows that the pulling spring V crosses the connecting axis C and the rotating body J moves away from the contact Gj. It is operation | movement explanatory drawing rotated in a direction.
The rotating body J rotates even when the door is stopped. 7 (a1), FIG. 7 (a2), and FIG. 7 (a3), the door remains stationary.

The link Ab is rotatably supported around a support shaft Ia provided on the door D, and a wheel B is mounted. The wheel B moves along the sliding surface K provided on the rotating body J, and rotates the link Ab. The link Ab is rotated slowly by the speed reduction means Rj2, and the rotating body J is also rotated slowly. Whatever the resistance means to rotate the rotating body J slowly, it only resists the rotation of the rotating body J regardless of the rotation of the door, so the force that the pulling spring V exceeds the resistance to resist the rotation of the rotating body J Therefore, the rotating body J continues to rotate without stopping. The rotating body J rotates slowly, the door is decelerated, the door inertia force does not work, and the door is fully closed.
The link device in which the door and the door closer are not interlocked does not need to employ a reverse rotation preventing means. The resistance acting on the rotating body J may be a frictional resistance, and the rotating body J does not stop and may continue to rotate.

The frictional resistance Rg for decelerating the door increases with the maximum static frictional force when it stops small due to the kinetic frictional force when the door is moving. When the door is moving, if it stops small with the kinetic friction force, it increases with the maximum static friction force. The door may stop in the middle due to unforeseen circumstances such as a gust of wind, and the spring that biases the door will weaken as it rotates. Will remain.
On the other hand, since the rotating body J can move in an environment that does not stop in the middle, the spring that biases the rotating body J may be at least as long as the kinetic friction force even if weakened. become.

In the case of FIG. 7A immediately before full closing, the rotating body J is prevented from rotating in the direction of arrow A in the figure by a contact Gj (not shown), the pulling spring V pulls the door, and the door is fully closed.
In the case of FIG. 7B, the connection shaft C and the fixed support shaft Sa provided on the door frame W are connected by two links. The rotating body JJ swings between the hit G1 and the hit G2 provided on the rotating body J. Until the rotating body J starts to rotate in the direction of the arrow a in the drawing and comes into contact with G1, it rotates without rotating the rotating body JJ and without rotating the door.
FIG. 7B provides a link device in which the door and the door closer are linked to a range in which the door closer continues to operate without moving the door.

Fig. 8 shows a door closer that operates in the range (A) and operates in the range (I) from the rotating device with the point of action close to the pivot O to the fully closed device with the point of action as the operating point. During the relay, the door closer keeps driving without moving the door.
In both FIG. 7 and FIG. 8, the force Fd acting on the door at the time of relay is a switching range in which the switching force is discontinuously switched from a small force to a large force, and a resistance equal to or less than the large force is applied to the door. Even if the door is stopped, the door does not remain stopped. Even if a resistance acts on the door when switching to a large force, the door starts moving even if the force is less than the large force, and the resistance acting on the door does not have to be removed in the switching range.

Both FIG. 7 and FIG. 8 increase the time required for relaying the switching range to apply resistance to the door during relay, and the operation of the door closer does not include the operation to remove the resistance applied to the door even if delayed. If the resistance is automatically removed, such as a reverse rotation prevention means, the resistance acting on the door may be greater than the large force, and FIG. Has switched to great power.
7 and 8, if the resistance acts and stops in the range where the door is rotated with a small force before the switching range, it will remain stopped, but by increasing the switching range time, the door closer will move to the door. The range in which the door can be rotated only by the inertia of the door without rotating the door can be increased, and the range in which the door can be decelerated is widened.

The urging means of the rotating device and the fully-closed device of FIG. 8 are common, and are a push spring U built in a cylinder S that is attached to the door D. The push spring U biases the piston Ps from the cylinder S in the direction of pushing out the piston Ps in the direction of arrow A in the figure. The piston Ps reciprocates along a predetermined track parallel to the door surface, and the sliding surface K provided at the tip of the piston Ps moves along the wheel B mounted on the fixed support shaft Sw. In the rotating device of FIG. 1, the wheel B moves along the moving sliding surface K to which the wheel B is fixed. In the rotating device of FIG. 8, the sliding surface K moves along the moving wheel B to which the rotating shaft is fixed. To do.

The fixed support shaft Sw is provided in the vicinity of the pivot axis O, and the rotational resistance around the pivot axis O of the door increases as the point of action of the force Fd acting on the door approaches the pivot axis O. The acceleration of the door is reduced by the amount lost due to the rotational resistance around the door.
The line of action of the force Fb at which the sliding surface K presses the wheel B passes through the fixed support shaft Sw and rotates around Sw. In the figure, D90 indicates a door that is stationary by pressing the door stop Gw1, and the pressing direction of the pressing force Fb is reversed from the direction of pressing the door stop Gw1 to the direction of pressing the door stop Gw2 with D80 in the figure as a boundary. .

The wheel spindle Ib is provided on the piston Ps, and the wheel BB is mounted. The wheel BB presses the sliding surface K1 provided on the door frame W to fully close the door. In the range (A), the point of action of the force Fd acting on the door is close to the pivot axis O, the strength of the spring is strong, the resistance around the pivot axis O is large, and the force to turn the door is small. In the range (ii), it is far from the pivot axis O, and even if the spring loosens and weakens, the force to turn the door is large. Since the piston Ps moves away from the sliding surface K wheel B at the tip of the piston Ps in the switching range, the movement of the piston Ps in the direction of arrow A in the figure is small in (A) and large in (I).

In FIG. 8 (a1 to a3), Rj1 has the same structure as the decelerating means Rj1 shown in FIG. 1 so that the pressing spring U can expand and contract. The higher the speed at which the air in the cylinder S is discharged to the outside, the more the piston Ps resists movement in the direction of arrow A in the figure. In the figure, the resistance of Rj1 is small in (A) and large in (I). Prior to the time of latch contact, the resistance to the movement of the piston Ps is small until the wheel B is separated from the sliding surface K, and the resistance acts largely after the separation. The wheel BB contacts the sliding surface K1.
In FIG. 8 (b1 to b3), Rj1 has no air resistance in the movement of the piston Ps, and allows momentary expansion and contraction of the push spring U. In FIG. 8 (b1 to b3), Rj2 has the same structure as the speed reduction means Rj1 shown in FIG. There is no resistance to the movement of the piston Ps until the wheel B is separated from the sliding surface K before the latch contact, and the resistance acts greatly after the separation. The wheel B moves away from the sliding surface K, and the wheel BB contacts the sliding surface K1.

Since the movement of the piston Ps after the wheel B is separated from the sliding surface K is decelerated by the decelerating means Rj1 in FIG. 8 (a1 to a3) and by the decelerating means Rj2 in FIG. 8 (b1 to b3). The state where BB does not contact the sliding surface K1 continues for a long time.
In FIG. 8 (b1 to b3), the speed reduction means Rj2 starts from a predetermined opening of the door, but the movement of the piston Ps stops when the speed reduction means Rj2 starts, and the movement speed after the start is indicated by the arrow i in the figure of the piston Ps2. Follow the moving speed in the direction. The moving speed of the piston Ps2 can be adjusted appropriately. The piston Ps2 is a movement preventing means for moving the piston Ps backward.

The check valve K2 shown in FIGS. 8 (a1 to a3) is rotatably supported around a support shaft Ik provided on the door frame W, and is urged by a torsion spring Vk, as shown in FIG. 8 (a1). As described above, the sliding surface K1 is pressed and stopped. The check valve K2 permits the passage of the wheel BB when the door is closed, but does not allow the passage of the wheel BB when the door is opened, and moves the piston Ps in the direction opposite to the arrow A in the drawing to return to the initial position. .

When the wheel BB contacts the check valve K2 and revolves around the pivot axis O, the check valve K2 rotates greatly, and the torsion spring Vk resists the revolution of the wheel BB. If the force Fb to be pressed is made large enough to rotate the door while the wheel BB rotates the check valve K2 and receives the resistance of the torsion spring Vk, the check valve K2 will move in the direction indicated by the arrow A in FIG. Does not block movement. In a range where the door closer does not rotate the door, the door is decelerated due to resistance.
Eventually, the check valve K2 rotates around the support shaft Ik in the direction of the arrow C in the figure, and the force with which the check valve K2 presses the wheel BB increases, and the frictional force acting on the revolution of the wheel BB increases. However, the direction of the force acts in the direction in which the wheel BB moves in the direction of arrow A in the figure, and the wheel BB contacts the sliding surface K1.

The sliding surface K3 shown in FIG. 8 (a1 to a3) is provided on the door frame W so that when the door rotates at high speed, the wheel BB moves along the sliding surface K3 before the door is fully closed. To do.
As shown in FIG. 8 (a2), when the latch male part begins to dent, a large force is not required to move the wheel BB, and the wheel BB temporarily stops while the latch male part begins to dent. The force to start moving later is small. The wheel BB moves along the sliding surface K3 with the effect of the deceleration means Rj1, and the door is fully closed. There is almost no impact sound when fully closed.
In FIG. 8 (b1 to b3), a check valve K2 and a sliding surface K3 (not shown) function in the same manner as in FIG. 8 (a1 to a3), and the door is decelerated.

In the case of FIG. 8 (a1 to a3) and FIG. 8 (b1 to b3), the time during which the state in which the wheel B is separated from the sliding surface K and the wheel BB is not in contact with the sliding surface K1 is continued. Even if the door remains stopped, the piston Ps continues to move. Even if the door is stopped by the check valve K2, when the wheel B continues to move along the sliding surface K2 and eventually comes into contact with the sliding surface K1, the door starts to move.
The longer the time that the wheel B is away from the sliding surface K and the state where the wheel BB is not in contact with the sliding surface K1 is longer, the longer the state in which the door is not biased by the push spring U continues, and the door inertia force alone. The time for rotation becomes longer, the time for receiving the resistance of the torsion spring Vk becomes longer, and the door decelerates. FIG. 8 shows an embodiment of a door closer that does not move even when the door stops, as shown in FIGS. 3 and 4, but continues to move even when the door stops.

In FIG. 8 (b1 to b3), the length of time during which the state where the wheel B is separated from the sliding surface K and the wheel BB is not in contact with the sliding surface K1 can be freely adjusted by the speed reduction means Rj2. The time for moving along the check valve K2 and the time for moving along the sliding surface K3 can be freely adjusted.
Prior to the time of latch contact, the movement of the piston Ps can be temporarily stopped by the deceleration means Rj2, and the door B can be moved by the door inertia force so that the wheel B is separated from the sliding surface K. At this time, if the wheel BB rotates the check valve K2 and receives the resistance of the torsion spring Vk, even if the door decelerates and stops at this time, the wheel BB is not blocked by the check valve K2. The piston Ps1 is relatively integrated with the piston Ps2 and moves in the direction of arrow A in the figure, so that the wheel BB comes into contact with the sliding surface K1.

In the case of FIG. 8 (a1 to a3), the case of FIG. 8 (b1 to b3), even when the resistance of the torsion spring Vk is too large, the piston Ps1 moves and the wheel BB is moved even when the door is stopped. By moving along the sliding surface K1, the force Fd acting on the door can be set to “a magnitude for rotating the door while receiving the resistance of the torsion spring Vk”. In the range of (a), even if the vehicle is decelerated due to a large resistance, it does not stop.
As shown in FIG. 8 (a1 to a3), if the wheel B does not leave the sliding surface K before the latch contact, the door may stop before the force Fd acting on the door increases. Yes, it may stay stopped.

The wheel BB continues to move along the sliding surface K3 while rotating the check valve K2 to receive the resistance of the torsion spring Vk by rotating the check valve K2, and presses the sliding surface K1 to rotate the door. Otherwise, the door will remain stationary.
When the resistance of the torsion spring Vk is increased, the force of the push spring U needs to be increased. As a result, the door is further accelerated within the range (A), and the resistance of the deceleration means Rj1 needs to be increased. In order to correct the result of the acceleration of the door, it is necessary to further increase the force of the push spring U, and a vicious circle occurs.

As shown in Fig. 1 and Fig. 2, the link device in which the action line of the door inertia force and the axial center line Zj of the rotating body J are in the substantially moving direction has resistance and air resistance acting in the opposite direction with the door inertia force unchanged. As described above, when the resistance that disappears when the door stops is used to make the door move, the door closer does not move easily even if a large force is applied to the door.
In both the embodiment shown in FIG. 8 (a1 to a3) and the embodiment shown in FIG. 8 (b1 to b3), depending on the resistance of the torsion spring Vk, the movement of the piston ps stops and the door remains stopped. Become. Even if the piston Ps2 is retracted without turning the door in FIG. 8 (b1 to b3), if the piston Ps stops without being released from the resistance of the torsion spring Vk, the door remains stopped.

As shown in the embodiment of FIG. 6, when the contact for preventing the rotation of the door is retracted, even if the resistance for preventing the rotation of the door is large, it is released, so even if the door stops, the door does not remain stopped. . As in the embodiment of FIG. 8, when the contact for preventing the door closer from rotating is retracted, the resistance for preventing the door from rotating is not released. Therefore, if the door closer stops, the door remains stopped.

The speed reducing means Rj1 of FIG. 8 (a1 to a3) depresses the piston Ps by the speed reducing means Rj1 because the sliding surface K provided at the tip of the piston Ps moves away from the wheel B and starts to move at a high speed. Starts automatically, but unless the sliding surface K of the piston Ps is separated from the wheel B, the deceleration of the piston Ps by the deceleration means Rj1 does not start.
8 (b1 to b3) has no resistance to the movement of the piston Ps, so even if the sliding surface K of the piston Ps moves away from the wheel B, until the piston Ps becomes relatively integral with the piston Ps2. The deceleration of the piston Ps by the deceleration means Rj1 does not start. Even if the sliding surface K of the piston Ps is not separated from the wheel B, if the piston Ps becomes relatively integrated with the piston Ps2, the deceleration of the piston Ps by the deceleration means Rj1 starts.

The speed reduction means Rj2 shown in FIG. 8 (b1 to b3) has the same structure as the speed reduction means Rj1 shown in FIG. 8 (a1 to a3), and has a built-in pull spring V instead of the push spring U. It is slowly housed in the cylinder S2 and is attached to the door D. The piston Ps2 is provided with a support shaft Irg, and a ratchet claw Qi is rotatably supported on the support shaft Irg.
Pg is attached to the piston Ps, the tip of the contact Pg moves along the sliding surface Kq provided on the ratchet claw Qi, the torsion spring Vq biases the ratchet claw Qi, and the sliding surface Kg hits the tip of the Pg Press the part. As the piston Ps moves in the direction opposite to the arrow A in the figure, the piston Ps2 is moved in the direction opposite to the arrow A in the figure while engaging with the starting end Kq1 of the sliding surface Kq.

FIG. 8 (b1) shows that the tip of the ratchet claw Qi is moved to the ratchet blade Qd while the tip of the ratchet claw Qi gets over the ratchet blade Qd attached to the door and the piston Ps moves in the direction of the arrow a in the figure. The standby state is shown in which the piston Ps2 is locked and does not move along the cylinder S2. When the piston Ps moves in the direction of arrow A in the figure, the tip of the contact Pg moves along the sliding surface Kq. FIG. 8 (b2) shows a state in which the leading end of the contact Pg comes into contact with the terminal end Kq of the sliding surface Kq to push up the ratchet pawl Qi and the leading end of the ratchet pawl Qi is separated from the ratchet blade Qd. The contact Pg engages with the piston Ps2 at a predetermined opening of the door, the piston Ps stops once, and the subsequent piston Ps starts moving at a low speed. The moving speed of the piston Ps becomes the moving speed of the piston Ps2. FIG. 8 (b3) shows that the piston Ps and the piston Ps2 are in a relative state until the door is fully closed with the leading end of the contact Pg abutting on the terminal end Kq of the sliding surface Kq and the ratchet pawl Qi being pushed up. The state which moved as a whole is shown.

FIG. 8A3 shows a state in which the check valve K2 contacts the sliding surface K1 when the door is fully closed. When the fully closed door is opened, the wheel BB moves along the reverse side of the check valve K2 that moves along the door closing, and the position of the piston Ps is determined when the door is closed. The wheel BB returns to the position accommodated in the cylinder S further than the position when the wheel BB contacts the check valve K2.
The door stop Gw1 shown in FIG. 8 (a3) is a door stop having a built-in push spring Ug, and the door remains stationary without coming into contact with the door stop Gw1. The force that the push spring Ug pushes back the door balances and the door stops. A door that is stationary at a position just before the fully closed position is convenient because the door can be opened without turning the door knob. If the door that is stationary at the position immediately before full closing is forcibly pushed in by hand, the latch male part Rd is accommodated in the latch female part Rw as shown in FIG.
Even if the door contact Gw1 does not include the push spring Ug, the door that is stationary at the position before full closing can be distorted and pushed into the position where the latch male part Rd is accommodated in the latch female part Rw.

The door of Patent Document 1 is characterized by the structure of the link device. The door rotates slightly in the range (ii) and the door closer operates greatly. However, the large operation of the door closer in the range (ii) ends instantly. By resisting the large operation of the door closer and lengthening the operation time of the door closer, it is possible to reduce the rotational speed of the door so that it takes time for the small rotation of the door, but the structure of the link device ( 9), the door can be decelerated by converting the small rotation of the door into a large operation of the door closer and decelerating the large operation as shown in FIG.

As shown in FIG. 9 (a2), the door D that rotates about the pivot axis O mounts the wheel B at a position far from the pivot axis O. The rotating body J rotates about the fixed support shaft Sw, and the wheel B moves on the fixed support shaft Sw while sliding on the outer edge portion of the rotating body J. Even if the rotation of the door D is small, the farther away the wheel B is from the pivot O, the greater the movement of the wheel B, and the closer the position where the wheel B slides to the rotating body J is closer to the fixed support shaft Sw, The rotating body J rotates greatly. In this case, a small rotation of the door D is converted into a large rotation of the rotating body J.

In FIG. 9 (a1), the wheel B is mounted on the rotating body J, and the door D has a sliding surface K. In FIG. 9B, the wheel B is mounted on the door D, and the rotating body J has a sliding surface K.
The shape of the sliding surface K shown in FIG. 9 (a1) is explained in FIG. 1, and the line of action of the force Fb that the sliding surface K presses the wheel B is fixed as shown in FIG. If the constant distance from the axis Sw is maintained and the constant distance is small, a small rotation of the door D is converted into a large rotation of the rotating body J.
As the shape of the sliding surface K shown in FIG. 9B introduces the drawing method in Patent Document 1, the line of action of the force Fb that the sliding surface K presses the wheel B is constant with the fixed support shaft Sw. If the distance is maintained and the certain distance is small, a small rotation of the door D is converted into a large rotation of the rotating body J.

9 (a1) and FIG. 9 (b), the pressing force Fb corresponds to the door inertia force, and the rotating body J has a large door inertia in the entire section in which the wheel B moves along the sliding surface K. It rotates with a small force while supporting the force.
In all the sections, assuming that the rotating body J is interlocked with the door D and is energized in the direction in which the rotating body J moves together with the door D, the door D rotates slowly according to the speed of the rotating body J. To do. The rotating body J is the above-described reverse rotation preventing means. 9 (a3) and FIG. 9 (b3), after the door D is decelerated, the wheel B moves away from the sliding surface K, and the resistance that continues to act on the door D is removed.

The speed reducing means employed here converts rotation into pendulum motion in FIGS. 9 (a) and 9 (b). In FIG. 9C and FIG. 9D, the rotation is converted into a linear reciprocating motion. Both are reciprocating movements, the movement speed becomes zero at the position where the movement direction of the reciprocating movement is reversed, the movement speed is accelerated from zero, and when it reaches the maximum speed, it is reversed from the advancing direction to the returning direction, Since the movement speed suddenly becomes zero, the rotation repeats momentary and intermittent stops. If the reciprocating object has a weight, a large dynamic inertia and a large static inertia are repeated.

9 (a1) and 9 (b), the link A is a pendulum swinging about the support shaft Ia, and a heavy object W is attached to the tip.
In FIG. 9 (a2), the rotating body J that rotates greatly includes a plurality of teeth G. The link A is mounted with a wheel B at the intermediate portion and is urged by a push spring U in a direction in which the tooth G is pressed. Each time the rotating body J rotates and the wheel B gets over the plurality of teeth G, the link A vibrates.
In FIG. 9B, the link A is provided with a connecting shaft P at the intermediate portion, the wheel B is mounted on the connecting shaft C provided at the tip, and is urged by the pressing spring U in the direction in which the teeth G are pressed. The link Ab connects the connecting shaft Cc provided on the wheel B and the connecting shaft P, and converts the circular motion of the connecting shaft Cc into the pendulum motion of the link A. The rotation of the wheel B is delayed, the speed at which the wheel B moves on the sliding surface K is delayed, and the rotation of the rotating body J and the door D is delayed.

9 (c) and 9 (d), the link A includes a support shaft Cc, and the support shaft C is a support shaft Cc that moves circularly about the connection shaft C in FIG. 9 (b). In FIG. 9C, the link A is mounted with the slider B, and the slider B reciprocates linearly along the groove M provided in the fixed portion W.
In FIG. 9D, the link A is equipped with a piston Ps, and the piston Ps reciprocates linearly in a cylinder S that swings around a support shaft Is provided on the fixed portion W.

A door that employs frictional resistance as a deceleration means will remain stationary if it stops during movement. For example, when the brake shoe decelerates due to friction, the resistance is a force that reduces the force Fd acting on the door. If the resistance is greater than the force Fd acting on the door, the door does not move. The force Fd acting on the door is positive and accelerates, is zero and moves at a constant speed or stops, is negative and decelerates. At the position where the door decelerates, the force Fd acting on the door is negative, and when the door stops at the position where it decelerates, it does not start again. If friction resistance is used, there is an effect of reducing acceleration, but when the door stops trying to decelerate, the door remains stopped and does not start again.

The frictional resistance can reduce acceleration even if the door cannot be decelerated without stopping with the door. In the door of Patent Document 1, even in the range (A), the force Fd acting on the door strongly presses the pivot O, the rotational resistance around the pivot O increases, and the strain energy of the spring is greatly consumed for friction loss. The feature is that the acceleration of the door is reduced. In the range of (A), the acceleration is small, the speed at the time of latch contact is kept small, and the work is further depressed to further decelerate and quietly fully close.
In this way, the force exceeding the frictional resistance can continue to be applied to reduce acceleration, and even if frictional resistance is adopted as the door deceleration means, there is nothing to stop the door in the middle of movement and it must be stopped in the middle of movement. There is no problem.

Even if a force smaller than the frictional resistance acts to decelerate, it continues to move until it stops. An object that is decelerating is moving backward in a direction in which the force works when viewed from a place where it is moving at a constant speed, and continues to move until the speed becomes zero and becomes a constant speed movement.
Like a rotation prevention means that moves backward, a speed reducer that moves with a spring separate from the door can be changed in a way that stops in the middle of movement, and even if you decelerate using frictional resistance, within a fixed time If you keep moving, don't leave the door stopped.

In the door of Patent Document 1, the rotating body J operates greatly within the range of (Yes). However, the rotation of the rotating body J is completed in an instant if there is no work due to resistance such as friction loss.
The door shown in FIG. 10 converts a small rotation of the door into a large rotation of the gear by a reduction gear using a gear. The more small rotations are converted to larger rotations, the more times the gears rub against each other, which resists small door rotations.

Unlike air resistance, the frictional resistance caused by the friction between objects does not stop when the door stops. Therefore, it cannot stop until the door is fully closed. Even when the spring force is weakened, a force exceeding the frictional resistance is required, and high speed rotation of the reduction gear using a gear is inevitable.

The door shown in FIG. 10 is a door disclosed in Patent Document 1, and the speed reducer using gears has little rotation in the range (A) and operates almost in the range (I). It is only necessary to keep exercising for a short time in the range (ii), and since it is already in the motion state within the range (ii), it can move with a relatively small force.
The door of Patent Document 1 does not use frictional resistance, and suppresses the acceleration of the door with such a small force that the door remains stationary. The door in Fig. 10 uses frictional resistance to suppress the door acceleration with a strong force that does not stop the door, and the door will not stop even if the door acceleration is reduced. .

FIG. 10 is an explanatory view of the operation of the door closer attached to the back side of the fully closed door. The rotating body J rotates about the fixed support shaft Sw in the direction of arrow A in the figure, and the door D shows the axis O about the pivot O. Rotate in the direction of arrow b.
FIG. 10 (a) is a sliding pair device similar to FIG. 1, and the wheel B mounted on the rotating body J moves along the sliding surface K or the deceleration sliding surface KK provided on the door D. FIG.
FIG. 10 (b) is a link device of a turning pair similar to FIG.

As shown in Fig. 10, the door closer attached to the back side of the door has a point of action Fd acting on the door away from the pivot O by the thickness of the door. It is necessary to slow down even within the range of (a).
FIG. 10 (a) converts a slight rotation of the rotating body J into a plurality of rotations of the gear G3. The gear G0 attached to the rotating body J and rotated around the fixed support shaft Sw is a gear. It is transmitted to the gear G3 via G1, G2, and so on.
The outer edge portion shape of the rotating body J shown in FIG. 10 (b) is the same shape as the sliding surface K shown in FIG. 9 (b), and the rotating body J rotates around the fixed support shaft Sww. The gear Bg mounted on the rotating body J moves along a plurality of teeth Kg provided on the outer edge of the rotating body J. The rotation less than a quarter of the rotation of the rotating body J is converted into a plurality of rotations of the gear Bg.

A sliding surface K2 shown in FIG. 10A is rotatably supported around a support shaft Ik provided on the door frame W, is urged by a pressing spring U, and is pressed by a wheel BB mounted on the door D. Decelerate the door. The sliding surface K2 shown in FIG. 10B is rotatably supported around the connection shaft C, is urged by the pressing spring U, is pressed against the rotating body J, and decelerates the door.
In both cases, the door that accelerates and rotates in the range of (A) is decelerated so rapidly that it is stopped almost before the full-closed dimension. The degree of deceleration is independent of the rotational speed of the door at the time of latch contact. The pressing spring U expands and contracts to a certain extent.

FIG. 10 (a1) is an operation explanatory view when the pressing spring U starts to expand and contract, and the wheel B that has moved along the sliding surface K in the range of (A) moves to the deceleration sliding surface KK, Slow down the door. The door closer connecting the door D and the door frame W at the connecting portion of the sliding pair having the sliding surface K and the speed reducing sliding surface KK has a range in which the door is not rotated while acting on the door, and FIG. ) After deceleration, it automatically returns to the sliding surface K and fully closes the door. Also in FIG. 10 (a2), when the full closing force acts on the door in FIG. 10 (b2), the wheel B moves away from the sliding surface K, and the resistance acting on the door is released. In the range of (ii), the axis Zj of the rotating body J is substantially perpendicular to the door surface, and the axis of the rotating body J is similar to the door that is not a door of Patent Document 1 shown in FIGS. The core wire Zj is not substantially parallel to the door surface.

FIG. 11 shows a moving device that moves by a spring, which is a device in which a spring slowly expands and contracts and continues to move for a long time, and does not employ air resistance.
Both the door and the speed reducer of Patent Document 1 do not end in a moment when the springs expand and contract, but move slowly when they expand and contract slowly.
In a device that moves with a spring, the strain energy of the spring is converted into work that resists the kinetic energy of the door or device, and the amount converted into kinetic energy is reduced by the amount converted into work that resists. Less. The resistance becomes greater than the force of the spring, and the kinetic energy is reduced to decelerate. If you don't slow down and remove the resistance, you'll stay still, but if you remove it, it starts again.

FIG. 11 shows an apparatus for slowly moving the moving body J by the elastic expansion and contraction of the spring, and includes means for delaying the movement of the moving body J. The means for delaying the movement of the moving body J is a spring different from the spring for moving the moving body J and includes means for releasing the means for delaying the movement of the moving body J by itself.
When the spring force acts on the moving body J and starts to move, even if resistance is applied, it continues to accelerate and does not decelerate.
As the above-described door closer is provided with a range in which the force for rotating the door is blocked, the speed reduction unit functions while the force for moving the moving body J is cut off, and when the function of the speed reduction unit is released, Mobile object J starts to move again. The force for moving the moving body J and the force for decelerating work alternately, and the moving body J repeats acceleration and deceleration. Both the spring that moves the moving body J and the spring that moves the deceleration means repeatedly stop and extend, and gradually lose power.

The device that applies resistance to the moving body J causes resistance by itself and releases the resistance by itself, like the movement preventing means that moves backward.
As explained in FIG. 9, if the moving body J repeats moving and stopping, the dynamic inertial force acting on the moving body J disappears every time it stops, and it is forced to grow from zero and does not increase.
In order to decelerate the door, the range in which resistance is applied is effective with the force to rotate the door cut off, and the door is rotated with the resistance applied for as long as possible without rotating the door. By delaying the time when the force begins to act again, the device will continue to move for a long time.

By making the force acting in the opposite direction to the force of the spring, such as friction resistance, on the device that moves by the spring acts as small as possible over multiple times, the strain energy of the spring supplied to the door and device can be as much as possible By supplying a small number of times, it can be a device that keeps moving for a long time.
If the stored strain energy of the spring is gradually reduced instead of all at once, as in the operation in the range (a) of the door of Patent Document 1, the speed change of the device becomes small. If you increase the natural length of the spring or move the spring mounting part closer to the rotating shaft to reduce the amount of expansion and contraction of the spring so that there is little change in the magnitude of the spring force before and after work, the spring distortion The decrease in energy is small.

A watch is a device that keeps moving for a long time by alternately stopping and moving. However, the watch cannot be moved while supporting the inertial force of the door with the small force of the spring. Alternatively, it cannot be a switch for starting the fully-closed device after a long time has elapsed. The apparatus shown in FIG. 11 employs a strong spring and does not end operation in an instant. In addition, by supporting the dynamic inertia force so that it does not remain even if it stops in the middle, it resists greatly when the dynamic inertia force is large and the dynamic inertia force is large, and resists completely when the exercise speed stops small. I try not to.

In FIG. 11, a link A is rotatably supported around a connection shaft C provided in the moving body J shown in FIG. Installed. The link A is urged by a spring V (not shown) so as to rotate in the direction of arrow A in the figure with the connection shaft C as an axis.
The track Zm is the axis of the groove M (not shown), and the connecting shaft C is moved along the groove M in the direction of the arrow B by the urging means Fc (not shown), and the connecting axis C is moved in the direction of the arrow B As a result, the wheel support shaft Ib moves along the track Zi in the direction indicated by the arrow C in the figure.
The biasing means Fc (not shown) that moves the connecting shaft C along the groove M in the direction indicated by the arrow B is prepared separately from the spring V (not shown) that rotates the link A in the direction indicated by the arrow A in the figure. Is done.

The wheel B moves along the sliding surface K while pressing the sliding surface K, and decelerates the moving speed of the connecting shaft C in the direction of arrow B in the figure. The subscript indicates the positional relationship between the connecting shaft C moving with time, for example, B0 indicates the position of the wheel B when the connecting shaft C starts to decelerate at the entrance of the sliding surface K, and B1 Indicates the position of the wheel B in the middle of the sliding surface K and during deceleration, and B1 indicates the position of the wheel B at the exit of the sliding surface K and at the end of deceleration.

In FIG. 11A, the wheel B moves along the rising portion K of the track on the stairs, and strain energy is stored in the spring V (not shown). The movement of the connecting shaft C is less than when the wheel B moves along the flat portions KK0, KK2 of the track on the stairs, and the energy of the biasing means (not shown) moves to the spring V, so that the connecting shaft C decelerates. .
FIG. 11A1 is an operation explanatory diagram when there is one link attached to the moving body J and one wheel B. FIG. 11 (a2) and 11 (a3) are operation explanatory views when there are 13 links and 3 wheels B attached to the moving body J, and FIG. 11 (a4) is a movement that rotates around the pivot axis O. FIG. 6 is an operation explanatory diagram when a connecting shaft C is provided at the tip of the body J and the connecting shaft C follows a circular orbit.

As shown in FIG. 11 (a2), the wheel B that was at the entrance position of the rising portion K moves to a position where it can escape from the rising portion K, as shown in FIG. At the same time as exiting K, the wheel BB following the wheel B rises and enters the entrance of the portion K. In this way, the succeeding wheels are sequentially replaced and moved along the rising portion K, so that the connecting shaft C repeats acceleration and deceleration a plurality of times. Further, the urging means and the spring (not shown) operate alternately and continuously to act on the connecting shaft C, and the connecting shaft C continues to move.
In FIG. 11 (a4), the speed is reduced each time one wheel B gets over the rising portions of a plurality of blades arranged on an arc centered on the pivot axis O.

11 (b) and 11 (c), the sliding surface K is an arc centered on the point C0 on the locus of the connecting axis C, and the wheel B is moving along the sliding surface K. In the meantime, the connecting axis C stops.
In FIG. 11A, each time the wheel B moves along the sliding surface K and strain energy is stored in the spring V (not shown), the force of the biasing means Fc (not shown) is required. 11 (b) and 11 (c), while the wheel B is moving along the sliding surface K, the urging means (not shown) moves with the force already stored in the spring V (not shown). Fc does not work. The force of the urging means Fc (not shown) is smaller than that in FIG.
The direction in which the wheel B is moved along the sliding surface K by being biased by the spring V (not shown) is the direction in which the moving body J is returned to the opposite direction to the arrow B in the figure even if the movement of the moving body J is stopped. Rather, it is a direction that follows the moving direction of the moving body J and resists the rotating body J while moving by itself in the moving direction by an urging means (not shown) in the same manner as the movement preventing means that moves backward, and releases the resistance by itself. .

While the wheel B is not moving along the sliding surface K, the wheel B moves while pressing the sliding surface KK by a spring V (not shown). When leaving the sliding surface KK0, the wheel B revolves around the corner KKs and moves along the sliding surface KK1, and the wheel B tries to leave the sliding surface KK by the force of the spring V (not shown). Don't do it. However, when the connecting shaft C moves at high speed in the direction of arrow B in the figure, the wheel B moves away from the sliding surface KK and moves to the sliding surface K. The faster the connecting shaft C moves, the longer the distance that the wheel B moves along the sliding surface K, and the longer the stop time of the connecting shaft C.

The shorter the distance between the corner KKs and the sliding surface K, the shorter the time for the wheel B to move away from the sliding surface KK and to the sliding surface K, and the position where the wheel B contacts the sliding surface K slides. Near the starting end Ks of the moving surface K, the distance that the wheel B moves along the sliding surface K becomes longer.
When the connecting shaft C is moved in the opposite direction to the arrow B in the drawing to return the device to the initial state, the wheel B moves along the sliding surface KK to the arrow in the drawing, but the sliding surface passing through the corner KKs. As the distance between the corner KKs and the sliding surface K is smaller, the sliding surface KK approaches the parallel to the sliding surface K and approaches a circle centered on the point C0. While the wheel B is moving along the sliding surface KK, which is a circle centered on the point C0, the connecting shaft C stops. In other words, the connecting axis C cannot move beyond the point C0.

In FIG. 11B, the track of the connecting shaft C is changed without changing the sliding surface KK. The link AA is rotatably supported around a support shaft Iaa provided on the moving body J, and the connection shaft C is provided at the tip of the link AA. The link AA swings between a position abutting against the contact G1 provided on the moving body J and a position abutting against the contact G2, and as shown in FIG. 11 (b1), the connection axis C is in the direction of arrow B in the figure. When moving, it hits G1 with the force pulling the wheel B. As shown in FIG. 11 (b2), when the connecting shaft C moves in the direction opposite to the arrow B in the figure, the force that pushes the wheel B abuts against the contact G2, and the point C0 moves to the position of the point C00 and is connected. The trajectory of axis C changes. A circle Rc00 is a circle centered on the point C00, closer to the point C00 than the track Zi, and the wheel B moves along the sliding surface KK, so that the rotating body J can move.

In FIG. 11C, the sliding surface KK is changed without changing the track of the connecting shaft C. The sliding surface KK is rotatably supported around the support shaft Ik, and waits at a position where the corner KKs abuts against the sliding surface KK1, as shown in FIG. 11 (c1). As shown in FIG. 11 (c1), the wheel B contacting the corner KKs moves in the direction indicated by the arrow C in the figure, and the sliding surface KK1 rotates in the direction indicated by the arrow in the figure and contacts the sliding surface KK2. And stop. As shown in FIG. 11 (c2), when the wheel B revolves around the corner KKs, the sliding surface KK is pressed and rotated in the direction indicated by the arrow E in the figure. As shown in FIG. 11 (c3), the wheel B revolves in the direction indicated by the arrow C in the figure by the force of a spring V (not shown).
As shown in FIG. 11 (c1), when the connecting shaft C moves in the direction opposite to the arrow B in the drawing, the wheel B moves in the two directions in the drawing along the sliding surface KK1, and the rotating body J moves. I can do it.

As shown in FIGS. 11 (a2) and 11 (a3), in the case of FIGS. 11 (b) and 11 (c), by adding a plurality of wheels that follow the wheel B, The wheels can be switched to move along the rising portion K, and the moving body J stops a plurality of times and repeats stopping and moving.
In the case of FIG. 11 (c), the sliding surface KK vibrates and generates a sound each time the moving body J repeats stopping and moving when the subsequent wheels are sequentially replaced. In the case of FIG. The moving surface KK does not vibrate and does not emit sound.

FIG. 11D is a graph in which the vertical axis indicates the moving speed v of the moving body J and the horizontal axis indicates the time t, and the triangular waveform area indicates the moving distance of the rotating body J. The area of one triangular waveform in FIG. 11 (d1) and the sum of the areas of the plurality of triangular waveforms in FIG. 11 (d2) are the same, and the moving distance of the rotating body J is the same. FIG. 11 (d2) shows a case where the moving body J repeats stopping and moving a plurality of times. The longer the stop time of v = 0, and the shorter the stopping and moving, the more the speed increases. If the wheel is changed every time the wheel is changed, it takes a longer time for the rotating body J to move the same distance.

FIG. 12 includes a connecting shaft C that moves along the groove M, and a speed reduction unit that resists the movement of the connecting shaft C and releases the resistance itself so that the connecting shaft C starts moving again. Is an explanatory diagram of an apparatus that alternately and repeatedly moves and stops, and is provided separately from an urging means for moving the connecting shaft C and a spring V that resists the movement of the connecting shaft C and releases the resistance itself. The urging means and the spring V alternately act on the connecting shaft C. The urging means moves the connecting shaft C and expands / contracts the spring V so that the speed reducing means resists the movement of the connecting shaft C itself. Try to store the power to release resistance. The biasing means continues to move the connecting shaft C until the spring V automatically recovers and starts to resist the movement of the connecting shaft C, and the spring V starts to resist the moving of the connecting shaft C and releases the resistance itself. Until that time, the urging means is stopped.

In FIG. 12, a track Zm is an axial center line of a groove M (not shown), and the connecting shaft C is moved along the groove M in the direction of the arrow B by the urging means Fc (not shown). The link A is rotatably supported around the connection axis C, and the wheel B is mounted on the wheel support shaft Ib provided at the tip of the link A. The link A is urged by a spring V (not shown) so as to rotate in the direction of arrow A in the figure with the connection shaft C as an axis. As the connecting shaft C moves in the direction of arrow B in the figure, the wheel support shaft Ib moves in the direction of arrow C in the figure along the track Zi.

In FIG. 12, when the connecting shaft C moves in the direction of arrow B in the figure along the track Zm by the biasing means Fc (not shown), the wheel B moves while pressing along the sliding surface KK and the sliding surface K. When the wheel B moves along the sliding surface K while pressing the sliding surface KK, the link A rotates about the connecting shaft C in the direction opposite to the arrow A in the figure, and the force is stored in the spring V. It is done. When leaving the sliding surface KK, the wheel B revolves around the corner KKs and moves along the sliding surface K.
The sliding surface K is an arc centered at a point C0 on the locus of the connecting axis C, and the connecting shaft C stops while the wheel B is moving along the sliding surface K. The urging means Fc (not shown) that urges the connecting shaft C in the direction of arrow B in the figure does not work.
With the restoring force of the spring V stored when the wheel B moves on the sliding surface KK, the wheel B moves along the sliding surface K, and the link A rotates about the connection axis C in the direction of arrow A in the figure. To do.

FIGS. 12 (a1) and 12 (b1) are operation explanatory views of the link A, the wheel support shaft Ib, and the wheel B when one connecting shaft C moves along the track Zm.
In FIG. 12 (a2), FIG. 12 (a3), FIG. 12 (b2), and FIG. Three wheels B are attached to each A. 12 (a2), 12 (a3), 12 (b2), and 12 (b3) show three links A and three wheel spindles when the rotating body J moves along the track Zm. It is operation | movement explanatory drawing of Ib and the three wheels B. FIG.

In FIG. 12 (a2), the wheel B does not reciprocate on the same track as shown in FIG. The forward and backward passages of wheel B are different.
The sliding surface Kg is rotatably supported around a support shaft Ig provided on the fixed portion W, and is urged by the push spring U in a direction rotating around the support shaft Ig in the direction indicated by the arrow in FIG. It comes into contact with the moving surface Kw1 and stops.
The sliding surface Kg is also a check valve, and when the connecting shaft C moves in the direction of arrow B in the figure and the wheel B moves along the sliding surface Kg2, the sliding surface Kg does not rotate. The wheel B moves from the sliding surface Kw2 to the sliding surface KK with a course. When the connecting shaft C moves in the opposite direction to the arrow B in the figure and the wheel B moves along the sliding surface Kg1, the sliding surface Kg rotates, and the wheel B moves straight from the sliding surface Kg1. Move to sliding surface Kw1.

FIG. 13 is an explanatory diagram of the operation of a door that rotates while closing and moving repeatedly. The heavier the weight of the door is, the greater the dynamic inertia and the inertia of the door are working. It will take a long time to accelerate.
As shown in FIG. 13 (a), the door D is moved in the direction indicated by the arrow B in FIG. The wheel B moves along the track Zm provided on the door D and the sliding surface K provided on the door frame W simultaneously. The track Zm is the axis of the groove M and is a straight track passing through the pivot O. The sliding surface K is a stepped sliding surface, and is composed of a sliding surface KK parallel to a linear track passing through the pivot O and a circumferential sliding surface K of a circle centering on the pivot O.
The wheel B is moved by the pulling spring V in a direction away from the pivot O (in the direction of arrow A in the figure). At the same time, the urging means Fo moves in a direction away from the pivot axis O while pressing the sliding surface K and the sliding surface KK.

The connecting shaft C is provided on the door D, the rotating body J is rotatably supported around the connecting shaft C, and the spring V is rotated so that the rotating body J rotates about the connecting shaft C in the direction of arrow A in the figure. Energize. The connecting shaft P is provided with a rotating body J, the link A is rotatably supported around the connecting shaft P, and a wheel B is mounted on a wheel supporting shaft Ib provided at the tip. The wheel spindle Ib moves along a groove M provided in the door D.
When the wheel support shaft Ib moves along the groove M in the direction of the arrow a in the figure, both while the wheel B is moving along the sliding surface K and while it is moving along the sliding surface KK. The door D rotates intermittently in the direction indicated by the arrow B in the figure, and the wheel support shaft Ib, like the movement preventing means that moves backward, prevents the door D from rotating, while the door O rotates in the rotational direction of the door D. Rotate in the same direction around the axis.

As shown in FIG. 13 (b), while the wheel B is moving along the sliding surface KK, the door D is stopped parallel to the sliding surface KK and the track Zm. Although the force of the spring V is applied to move the wheel B, the urging means Fo (not shown) that urges the door D in the direction of arrow B in the figure does not work. When the wheel B finishes moving along the sliding surface KK, the wheel B moves away from the sliding surface KK and comes into contact with the sliding surface Kg.
As the door rotates at a higher speed with a larger door inertia force, the force with which the wheel B presses the sliding surface KK increases, and a greater frictional resistance acts on the movement of the wheel B. The time during which the wheel B is moving along the sliding surface KK is lengthened, and the time for the door to stop is lengthened. The effect of decelerating the door increases with the magnitude of the door inertia force.

The sliding surface Kg is parallel to the sliding surface K and faces the sliding surface K, and a passage is provided between the sliding surface K so that the wheel B can barely pass through circular movement about the pivot axis O as one center. The distance between the sliding surfaces Kg is a width that allows the wheel B to pass through, and the door can be opened during deceleration.
When the wheel B moves along the sliding surface Kg in the direction of the arrow B in the figure, the door is closed, the movement of the wheel support shaft Ib in the direction of the arrow a in the figure stops, and the force of the spring V does not work. In this way, the door is closed and rotated while repeating stop and rotation alternately. While the door B is slightly rotated, the wheel B moves a long distance along the sliding surface K, and as the number of times of alternately stopping and rotating is increased, a longer time elapses and the rotation speed of the door becomes slower.

The sliding surface K shown in FIG. 13B is rotatably supported around a support shaft Ik provided on the door frame W, is urged by a pressing spring U, and comes into contact with the contact Gk and is stationary. Each time the wheel B comes into contact with the sliding surface K, the push spring U contracts and absorbs the kinetic energy of the door, so that the impact when the door stops is reduced.
The wheel Bj is mounted on the connecting shaft P and moves along the sliding surface Kj provided on the door frame W when the door is opened, and the wheel B is brought close to the pivot O to bring the reduction gear of FIG. return.

In FIG. 14 (a), the connecting shaft C is urged by urging means (not shown), and the link A is swingable around the connecting shaft C that moves in the direction of the arrow B along the track Zm provided in the fixed portion W. The wheel B is mounted on the tip of the link A, and the wheel B moves along the sliding surfaces K1 to K5 provided in the fixed part W, and moves in the direction B while swinging left and right. The wheel B5 indicated by a solid line moves along a sliding surface K2 in a path sandwiched between the sliding surfaces K1 and K2.

The crossing angle Θak is an angle at which the axial center line Za of the link A intersects the sliding surface K. When the connecting axis C moves in the direction of the arrow B along the track Zm, the crossing angle Θak is a right angle or a right angle or more. If it is an obtuse angle, the wheel B stops, and if it is an acute angle, the wheel B moves and the connecting shaft C also moves. The intersection angle Θak increases as the wheel B moves along the sliding surface K, and when the wheel B approaches the tip KK2 of the sliding surface K2, the intersection angle Θak approaches a right angle.

In the embodiments of FIGS. 11, 12, and 13, when the wheel B moves along the sliding surface K, the connecting shaft C substantially stops and the rotation of the door D substantially stops. As the wheel B moves along the sliding surface K, the connecting shaft C moves along the track Zm. In this case, urging means for moving the wheel B along the sliding surface K is not necessary.
In the embodiment of FIGS. 11, 12, and 13, the connecting shaft C or the door D repeatedly stops and moves, but in FIG. 14A, the low speed motion and the high speed motion are repeated.

In these embodiments, if the connecting shaft C or the door D is referred to as a moving body and the wheel B is referred to as a moving body, the moving body moves in a direction substantially perpendicular to the direction in which the moving body travels. Proceed slightly in the direction of travel. A moving body can move with a small force even if it greatly resists the progress of the moving body.
A door is a general term for a moving body, and a moving object having a mass has kinetic energy. When the object abuts against an elastic body such as a spring, the elastic body is deformed and the kinetic energy is converted into strain energy of the elastic body. The movement speed of the moving body decreases. The door D is decelerated by expanding and contracting a spring.

5 (b) and 5 (c), the wheel B is a moving body, and the single gear Jk comes into contact with and disengages from the wheel B and is relatively integrated with the wheel B while being in contact with the wheel B. It is a moving body that moves in the moving direction of B. The moving body and the moving body that move in the same direction at different speeds are each provided with a biasing means that biases them in the respective moving directions separately, and move at a high speed when moving relatively integrally while contacting each other. One of the moving body and the moving body is decelerated to the other moving at a low speed, and the other is accelerated. The kinetic energy of the moving body is converted into the kinetic energy of the moving body, and the moving speed of the moving body decreases.
5 (b) and 5 (c), the wheel B is also a contact portion where the door D contacts and separates from a part of the speed reducer, and the moving body contacts and separates from a part of the speed reducer. The moving body that is also a contact portion and the moving body comes into contact with and separates from the moving body is also a part of the speed reduction device.

In FIG. 14A, the connecting shaft C is a moving body C that moves at a high speed, and the wheel B is a moving body B that moves at a low speed in the moving direction of the connecting shaft C. As in FIGS. 5B and 5C, the moving body C and the moving body B that move in the same direction at different speeds move relatively integrally, and the moving body C that moves at high speed. Is decelerated to the moving body B that moves.
If there is an urging means for always urging the axis A Za of the link A so as to overlap the track Zm, the moving body B will not stop if the moving body C stops due to the resistance of the moving body B. The moving body C never stops and keeps moving.

Also in FIG. 11 (a), when the wheel B moves along the sliding surface KK in FIG. 12, the restoring force is stored in the spring V (not shown) and decelerates, but when the moving force of the moving body J is small, The movement of the moving body J may remain stopped. In FIG. 14 (a), when the urging means for urging the link A is a spring, the direction in which the wheel B moves along the sliding surface KK by the restoring force of the spring is when the connecting shaft C advances. The direction in which the wheel B moves along the sliding surface KK when the connecting shaft C advances is not the direction in which force is stored in the spring.

In FIG. 14A, the position of the wheel B when the wheel B abuts against the sliding surface K2 is indicated by B4, and the position of the connecting shaft C is indicated by C4. A position where the wheel B starts to revolve around the tip portion Ke2 is shown in B5, and a position of the connecting shaft C at that time is shown in C5. The distance u2 between the connection axis C4 and the connection axis C5 shown on the track Zm is the movement distance of the connection axis C when the wheel B moves in the direction intersecting the track Zm along the sliding surface K2. . Further, the distance v2 between the connection axis C5 and the connection axis C7 shown on the track X is a movement distance of the connection shaft C when the wheel B is large in the track X direction and the wheel B revolves around the tip Ke2. It is.

The distance between the front sliding surface and the rear sliding surface is, for example, the distance between the sliding surfaces K1 and K2 and a width greater than the diameter of the wheel B, so the distance v2 is larger than the moving distance u2. . In this way, when the wheel B moves in the direction of the arrow B while being meandered by being pulled by the connecting shaft C via the link A, when the wheel B changes direction to the left and right, the connecting shaft C moves greatly along the track Zm. To do.
When the wheel B changes direction from side to side, the speed of the wheel B in the direction perpendicular to the track Zm becomes zero, but the speed in the direction of the track Zm is large, and the spring V biasing the connecting shaft C expands and contracts instantly. Further, all of the strain energy of the spring V is converted into kinetic energy, and the connecting axis C is greatly accelerated. The acceleration in the range where the movement of the wheel B is not prevented by the sliding surface K is large.

14 (b1) and 14 (b2), the sliding surfaces K1 to K5 are rotatably supported around the supporting shafts Ik1 to Ik5 provided on the fixed portion W, and are urged by the pressing springs U1 to U5. And contact with G1 to G5. The distance between the front sliding surface K and the rear sliding surface K is, for example, the distance between the sliding surfaces K1 and K2 is approximately half the diameter of the wheel B.
The connecting shaft C is urged by a pulling spring V (not shown) and moves in the direction of the arrow B along the track Zm provided in the fixed portion W. The wheel B is pulled by the connecting shaft C via the link A.

As shown by a broken line in FIG. 14 (b1), when the wheel B is at a position far from the front end Ke1 on the sliding surface K1, the intersection angle Θak is an acute angle, and the wheel B while the intersection angle Θak approaches a right angle. Moves away from the spindle Ik1. The rotational moment around the support shaft Ik1 increases, and the sliding surface K1 rotates around the support shaft Ik1 in the direction of arrow A while contracting the push spring U1. The tip portion Ke1 moves in the direction of the arrow B by approximately half of the diameter of the wheel B and comes into contact with the tip portion Ke2 of the sliding surface K2. A wheel B3 indicated by a broken line indicates a state in which the wheel B3 is transferred from the sliding surface K1 onto the sliding surface K2.

FIG. 14B2 shows a state in which the wheel B3 has been transferred from the sliding surface K1 onto the sliding surface K2, and the sliding surface K1 has returned to the initial position. Just as the sliding surface K1 rotates around the support shaft Ik1, the sliding surface K2 rotates around the support shaft Ik2 in the direction of the arrow B while contracting the push spring U2, and the tip Ke1 is approximately half the diameter of the wheel B. The wheel B3 can move from the sliding surface K2 onto the sliding surface K3 by moving in the direction indicated by the arrow B and abutting against the tip portion Ke2 of the sliding surface K2.
In this way, the wheel B moves from the sliding surface K3 to the sliding surface K5, and when it moves away from the sliding surface K5, it does not resist the movement of the connecting shaft C in the direction of arrow B.

The distance between the connection axis C1 and the connection axis C3 shown on the track Zm is the movement distance of the connection axis C when the wheel B1 moves on the sliding surface K1, and is approximately half the diameter of the wheel B. . Similarly, the moving distance of the connecting shaft C when the wheel B3 moves from the sliding surface K1 to K2 is also approximately half the diameter of the wheel B. The moving distance of the connecting shaft C during the transition of the wheel B from the sliding surface K1 to the sliding surface K5 is smaller in FIG. 14 (b) than in FIG. 14 (a). When the movement distance of the connection axis C in FIG. 14B and the movement distance of the connection axis C in FIG. 14A are the same, the number of times that the wheel B changes direction to the left and right increases.

When the wheel B changes direction from side to side, in FIG. 14A, the wheel B moves greatly in parallel with the track Zm without receiving resistance and accelerates greatly. In FIG. 14B, the movement of the wheel B is accompanied by expansion and contraction of the push spring U, so that the wheel B decelerates. The moment when the wheel B changes to the next sliding surface K is when the push spring U starts to contract, and the connecting shaft C stops. Each time the pressing springs U1 to U5 are contracted sequentially, the connecting shaft C moves, and stops and moves alternately.
In the graph showing the relationship between the speed and time in FIG. 11 (d2), the speed of the connecting axis C is a discontinuous triangular waveform, the sum of the stop times is large, and the motion duration time is long.
The connecting axis C moves over a short distance over a long time. If a moving body that moves at a high speed in the same direction as the connecting axis C collides with the connecting axis C as a moving body C that moves at a low speed on the connecting axis C, the moving body will be decelerated integrally with the moving body C. Will move.

In FIG. 14C, the moving body J is urged so as to move in the direction of arrow B along the track Zm by urging means (not shown). A connecting shaft C and a connecting shaft CC are provided on the moving body J, and a link A and a link AA are rotatably supported around each of them. The link A and the link AA are each urged by a spring spring VV so that the link A and the link AA swing around the axis core line Zj of the moving body J, and the wheels B and BB attached to the distal ends of the links A and AA are centered on the axis core line Zj. Pendulum exercise.
Sliding surface K and sliding surface KK are arc-sliding surfaces in which wheel B and wheel BB move along with connecting shaft C and connecting shaft CC stopped, and the center of the arc is connected. This is the position where the axis C and the connecting axis CC stop.

The sliding surface K and the sliding surface KK are provided with a hole H and a hole HH through which the wheel B and the wheel BB can barely pass, respectively, around the shaft center line Zj. FIG. 14C2 shows a state where neither the wheel B nor the wheel BB is in the hole H or the hole HH, and a state where the moving body J cannot move. FIG. 14 (c3) shows a state in which the moving body J cannot move even if one of the wheel B and the wheel BB is on the hole H or the hole HH unless the other is on the hole H or the hole HH. FIG. 14 (c4) shows a state where both the wheel B and the wheel BB are stationary at a position where the wheel B and the wheel BB can pass through the hole H and the hole HH, and the wheel B and the wheel BB simultaneously pass through the hole H and the hole HH. Indicates the state that can move.

FIGS. 14 (c1) and 14 (c2) illustrate an apparatus in which the amplitude start timing is made different so that the link A and the link AA make an amplitude with different rotation angles. The rotating body Jb is rotatably supported around a support shaft S provided on the fixed portion W, and includes a circular sliding surface Kj centered on the support shaft S.
In FIG. 14 (c1), the wheels B and BB are urged by the spring spring VV and try to move in the direction of arrow A along the sliding surface K and the sliding surface KK, respectively, but the sliding surface Kj prevents this. doing. FIG. 14 (c2) shows a state where the sliding surface Kj rotates around the support shaft S in the direction of arrow C, the wheel BB has already moved in the direction of arrow B, and the wheel B is about to start moving with a delay. Is shown. FIG. 14 (c3) shows a state where both the wheel B and the wheel BB are moving away from the sliding surface Kj.

As long as the sliding surface K and the sliding surface KK are the above-described arcs, and the urging force of the mainspring spring VV is not weakened, the wheel B and the wheel BB continue to swing around the axis line Zj. The moving body J does not move while either the wheel B or the wheel BB is on the sliding surface K or the sliding surface KK.
If the amplitude start timings of the links A and AA are different and the amplitude cycle is the same, the wheels passing through the hole H or the hole HH are alternately switched, and both the wheel B and the wheel BB continue to amplitude for a long time. Even when one of the wheel B and the wheel BB finishes the amplitude motion and stops on the shaft core line Zj, the moving body J does not move while the other is not on the shaft core line Zj.
FIG. 14 (c4) shows a state in which both wheels B and BB have finished the amplitude motion and stopped at a position where they can pass through hole H and hole HH, and wheels B and BB simultaneously move through hole H and hole HH. The state where the body J moves is shown.

In the case of FIGS. 14 (a) and 14 (b), the moving body_J gradually moves and becomes means for gradually expanding and contracting the spring. In the case of FIG. 14 (c), the moving body_J has a long stop time, and as shown in FIG. 14 (c1), the moving body starts after the sliding surface Kj rotates and the apparatus of FIG. 14 (c) starts. _J takes a long time to start moving. When a certain device is switched on by the movement of the moving body_J, the device shown in FIG. 14C is switched on, and after a while, the certain device is switched on.
For example, when the sliding surface Kj rotates as shown in FIG. 14 (c1) at the same time as the brake is applied to the door, the movable body J starts to move as shown in FIG. The brake applied to the door can be released with a delay.

14 is not limited to the device shown in FIG. 14, and the deceleration device that suppresses the acceleration of the door that is moved by a spring supports a large door inertia force and generates a large force that finally switches on some device like the device shown in FIG. Therefore, it is not a device that keeps moving with the force of a weak spring like a watch, but a device that keeps moving for as long as possible with the force of a strong spring and does not stop halfway.
The device added to the door that is urged by these springs to rotate and close is a device that continues to move with a spring other than the spring that urges the door. Even if you support the inertial force of the door, it must not stop.

For this reason, a strong spring is used, which starts before the door is fully closed, and allows a long time to pass from the position just before the door is fully closed to the fully closed position. It is a device that finishes the operation before full closing.
It is a device that releases the resistance that was applied before the fully closed dimension before the fully closed dimension, or a device that switches on some device and starts some time after the device is switched on, After releasing the resistance, and after starting the switch for a while after starting the switch, it can continue to have a large force, and the door can be fully closed after the operation of the device is completed. I can do it.
These devices are also fully closed devices.

In FIG. 14, the rotation axis C of the pendulum movement is moved, and the sliding surface K is fixed to the fixed portion. However, FIG. 15 shows the sliding surface without the movement of the rotation axis C of the pendulum movement. K is the one that moves.
The rotating body J is urged by the push spring U and performs a pendulum motion about the fixed support shaft Sw provided on the fixed portion W. The wheel support shaft Ib and the wheel support shaft Ibb are provided on the rotating body J and are mounted with the wheel B and the wheel BB, respectively.
The moving body Jk is urged by the pulling spring V, moves in the direction of arrow B in the figure along the track Zm provided in the fixed portion W, and includes a plurality of sliding surfaces K1, K2, K3,. The shape of the sliding surfaces K1, K2, K3,... Is an arc centered on the fixed support shaft Sw, and the wheel BB slides along the sliding surfaces K1, K2, K3,. At that time, the moving body Jk stops. Each sliding surface K is equally divided and is attached to the base end portion Ks of the moving body Jk.

FIG. 15A1 is an operation explanatory diagram when the wheel BB is in the vicinity of the base end portion Ks3 of the sliding surface K3, the wheel BB starts to move along the sliding surface K3, and the moving body Jk stops. It is. The rotating body J rotates while the moving body Jk is stopped so that the wheel B is separated from the end portion Ke1 of the sliding surface K1. At this time, the fixed support shaft Sw, the wheel rotation shaft Ib, and the end portion Ke1 are arranged in a straight line.
A solid line B1 indicates the moment when the wheel B leaves the end portion Ke1, and B2 and B3 indicated by broken lines indicate a state in which the wheel B comes into contact with the next sliding surface K2 after leaving the end portion Ke1.
As soon as the wheel BB leaves the end portion Ke3, each sliding surface K begins to move, but soon after each sliding surface K moves, the wheel B comes into contact with the next sliding surface K2. Dashed lines B3 and BB3 indicate a state in which the wheel B is in contact with the sliding surface K2, and a state in which the wheel BB is separated from the sliding surface K3, before each sliding surface K moves.

Broken lines B2 and BB2 indicate a state immediately before the wheel BB is separated from the sliding surface K3, and indicate a state immediately before each sliding surface K is about to move.
The boundary line Xe is a trajectory of the end part Ke, and is divided into a region Ys that does not include the sliding surface K and a region Yk that includes the sliding surface K with the boundary line Xe as a boundary.
As shown in FIG. 15 (a2), the wheel BB once comes out to the region Ys by the urging of the pushing spring, but at the same time, each sliding surface K moves by the distance L1 by the urging of the pulling spring V and hits the wheel B. Touch.

The wheel B3 is pressed against the sliding surface K2, and the rotator J rotates in the direction of the arrow B so that the wheel BB enters the region Yk from the region Ys, but rotates behind the sliding surface K3.
When the wheel BB comes into contact with the back surface of the sliding surface K3, the rotating body J stops and each sliding surface K also stops, so that the wheel BB contacts the sliding surface K as shown in FIG. Reduce the wheel BB so that it does not hit the back. At this time, the distance between the position bb of the wheel BB farthest from the fixed support shaft Sw and the fixed support shaft Sw is not changed.

When the sliding surface K2 moves by the distance L1, the wheel BB crosses the boundary line Xe. As shown in FIG. 15 (a3), when the distance L2 further moves, the reduced wheel BB is included in the region Yk. The wheel B5 reaches the end portion Ke2 and starts to revolve around the end portion Ke2.
As shown in FIG. 15 (a4), when each sliding surface K is further moved by the distance L3, the wheel B6 indicated by the solid line is in contact with the boundary line Xe, and all of the wheels are included in the region Ys. If the distance L4 further moves, the wheels B7 and BB7 indicated by broken lines return to the positions B1 and BB1 shown in FIG. 15A, and the sum of L1, L2, L3, and L4 becomes the distance L between the sliding surfaces K. .

When the sliding surface K2 moves to the position of the sliding surface K1 in FIG. 15 (a1), the wheel BB begins to move along the sliding surface K4 behind the sliding surface K3 as shown in FIG. 15 (a4). The moving body Jk stops again.
Depending on the difference in strength between the push spring U and the tension spring V, the distance that the sliding surface K moves in contact with the wheel B varies. As the wheel B3 shown in FIG. 15 (a1), when the wheel B comes into contact with the sliding surface K3 not moving at all, the strain energy absorbed by the push spring U is maximum, and the moving body Jk is greatly decelerated.

FIG. 15 (b) is an example in which “rotating body Ja that is mounted with wheels Ba and BBa and rotates about fixed support shaft Swa” is added to rotating body J shown in FIG. 15 (a). Are the same size, and the wheel BBa and the wheel BB are the same size. The rotating body Ja and the rotating body J have the same shape and size.
When the position of the fixed support shaft Swa is set so that the wheel Ba revolves around the end portion Ke1 when the wheel B moves away from the end portion Ke1 as shown in FIG. 15 (b1), it is shown in FIG. 15 (b2). Thus, while each sliding surface K moves slightly, wheel Ba leaves | separates from the terminal part Ke1, and wheel BBa contact | abuts to the base end part Ks3, and stops each sliding surface. The wheel B comes into contact with the position where the sliding surface K2 slightly moves, and the push spring U starts to shrink from a state where it is greatly loosened. Further, while the sliding surfaces K slightly move, the moving body Jk is temporarily stopped twice by the wheels BB and BBa.

As shown in FIG. 15 (b3), when the wheel B starts to revolve around the end portion Ke2 and the pressing spring U finishes contracting, the wheel Ba is in the middle of the sliding surface K2 and the pressing spring Ua continues to contract. In this way, each sliding surface K moves greatly and the rotating bodies J and Ja rotate, and the strain energy of the tension spring V is greatly absorbed by the strain energy of the push spring Ua. Further, when each sliding surface K moves, the state returns to the initial state of FIG. 15 (b1), but FIG. 15 (b4) adds the rotating body Ja to the device of FIG. 15 (a) and the device of FIG. 15 (b1). As shown in FIG. 15, the apparatus shown in FIG. 15B1 further includes a rotating body Jb indicated by a broken line, and the number of times that the moving body Jk temporarily stops with respect to the moving distance of each sliding surface K increases.

The rotating body J shown in FIG. 15 performs the same work as an ankle that causes the escape wheel to alternately repeat stop and rotation in the timepiece.
The watch is a pendulum with a weak spring that keeps oscillating for a long time and consists of a mechanism in which the exchange of kinetic energy and potential energy continues forever, but the pendulum movement of the rotating body J shown in FIG. The pressing spring U is not contracted by the dynamic inertia force of the rotating body J, the kinetic energy of the rotating body J is replaced with the strain energy of the pressing spring U, and the strain energy of the replaced pressing spring U becomes the kinetic energy of the rotating body J. Therefore, the pendulum movement of the rotating body J will not continue.

In the watch, the strain energy of the mainspring is changed to the kinetic energy of the ankle to accelerate, whereas in the device shown in FIG. 15, the strain energy of the push spring decelerates the rotating body J and the moving body Jk.
The reciprocating motion of the pendulum movement of the rotating body J is different from the forward biasing means and the backward biasing means, and alternately acts on the pendulum movement. When one side acts, the other pauses, and when the forward movement is applied by the forward movement biasing means, the force of the backward movement biasing means is stored.

FIG. 16 is a reduction device that prevents the door spring from being pushed back by restoring the push spring U after the door spring is decelerated due to the dynamic inertia force of the door and decelerating the door, and the door is decelerated and temporarily stopped. It is explanatory drawing of the deceleration device which starts again after the push spring U contracts, decelerates the door and stops once.
In FIG. 16A, the wheel B provided in the door D abuts against the sliding surface K, the push spring U contracts, and the door D decelerates. In FIG. 16B, the sliding surface Kw contacts the wheel Bj, the rotating body Jb rotates, the wheel B mounted on the rotating body J contacts the sliding surface K, and the push spring U contracts. The door D decelerates.

The rotating body J is urged by the pulling spring V in a direction away from the contact Gc, and before the wheel B comes into contact with the sliding surface K, along the sliding surface Kb provided on the fixed portion W in FIG. It moves and moves along the sliding surface Kb provided in the door D in FIG.16 (b). When the wheel B comes into contact with the sliding surface K, the wheel B moves away from the sliding surface Kb.
In FIG. 16, the door inertia force is transmitted to the push spring U via the wheel B, but it is the door inertia force that restrains the wheel B at the “position for transmitting the power”. Presses the sliding surface K, and the pressing force Fb rotates the rotating body J in the direction in which the connecting shaft C hits the shaft and contacts the Gc. The winning Gc is provided on the door D.

While the door inertia force works and the rotating body J comes into contact with Gc and is stationary, the wheel B is restrained from moving from the position where the sliding surface K is pressed.
When the door stops and the door inertia force disappears, the restraint of the wheel B is released, the door inertia force does not press the wheel B, and the rotating body J rotates away from the contact Gc by the pulling spring V. The wheel B moves to a position where power is not transmitted. The restoring force of the pressing spring U does not act on the door.

In FIG. 5, as defined as “wheel B is moving body B and single gear Jk is moving body Jk”, in FIG. 16A and FIG. 16B, wheel B is moving. The sliding surface K is the moving body K. The moving body B and the sliding surface K are relatively integrated with each other via the contact b, and move in the same direction, and gradually decelerate as the pressing spring U contracts, and the motion when the pressing spring U is fully contracted. Body B stops temporarily.
The contact b moves in a direction perpendicular to the direction of motion by the tension spring V and force prepared in advance, the moving body B and the sliding surface K are separated, and the moving body B is released from the resistance of the push spring U. .
The pressing spring U contracts in accordance with the speed of the moving body B, and the resistance of the pressing spring U increases as the speed of the moving body B increases, and a longer time is required until the pressing spring U is fully contracted.

As shown in FIG. 16 (a1), the sliding surface K is pivotally supported around the pivot axis O, and is urged by the push spring U in the direction opposite to the arrow B in the drawing to contact with the contact Gk. Waiting in a quiescent state.
The door D rotates about the pivot O in the direction of arrow B in the figure. The rotating body J is rotatably supported around a connecting shaft C provided on the door D, and is urged by a pulling spring V in the direction of arrow A in the figure. A wheel B is mounted on a wheel spindle Ib provided at the tip, and the wheel B moves in the direction of arrow B in the figure while pressing the sliding surface Kb provided on the door frame W as the door D rotates. When the door D rotates at a high speed, the wheel B leaves the corner Kbs of the sliding surface Kb and comes into contact with the sliding surface K before the rotating body J rotates in the direction of the arrow A in the figure.

The sliding surface K comes into contact with the door D via the wheel B, and is relatively integrated with the door D and rotates away from the contact Gk. While the pressing spring U contracts, the kinetic energy of the door D is absorbed and the door D is decelerated.
Although the pressing spring U contracts and stores restoring force, the sliding surface K includes a reverse rotation preventing means for preventing the pressing spring U from restoring. The sliding surface K is provided with a sliding surface KK, and the rotating body JJ is rotatably supported around a support shaft Ij provided on the door frame W, and the rotating body JJ is urged by the pulling spring Vj to indicate an arrow in the figure. The wheel BB mounted on the rotating body JJ moves along the sliding surface KK. Although the sliding surface K rotates and the wheel BB moves along the sliding surface KK, the wheel BB moves along the sliding surface KK so that the sliding surface K does not rotate.

The action line of the force Fbb that the sliding surface KK presses the wheel BB passes near the support shaft Ij, and the wheel BB easily rotates with the small force of the pulling spring Vj along the sliding surface KK in the direction of arrow C in the figure. However, even if the sliding surface KK presses the wheel BB with a large force, it does not rotate easily. The wheel BB prevents the sliding surface K from rotating in the direction opposite to the arrow B in the figure.
At the same time as the expansion and contraction of the push spring U stops, the wheel BB stops and the restoration of the push spring U is prevented, and the sliding surface K prevents the door D from returning in the opening direction by the restoring force of the push spring U.

The stop of the push spring U is the stop of the door, and since the kinetic energy of the door D is lost at the stop, the wheel B has no force to press the sliding surface K, and the restoration of the push spring U is prevented. In addition, since the wheel BB presses the sliding surface KK and the force for contracting the pushing spring U does not work, the wheel B can move freely along the sliding surface K, and the pulling spring V can rotate the rotating body. J rotates and the wheel B moves away from the sliding surface K. The door D does not receive resistance but rotates closed.
The sliding surface K is a rotation preventing means that moves backward. When the door D decelerates and stops, the wheel B moves away from the sliding surface K, and the rotating rotation preventing means that acts on the door D is released. Door D does not remain stationary.

In FIG. 16A, one of the attachment portions of the push spring U is fixed and supported by the door frame W, while one of the attachment portions of the push spring U is fixed and supported by the door D in FIG. Also in FIG. 16A, the sliding surface K rotates about the pivot O provided on the door frame W, and rotates on the connection axis CC provided on the door D in FIG. 16B. The apparatus in FIG. 16A includes a part that attaches to the door D and a part that attaches to the door frame W, whereas the apparatus in FIG. 16B includes only a part that attaches to the door D.

As shown in FIG. 16B, the sliding surface K is urged around the connecting shaft CC in the direction opposite to the arrow B in the drawing, and abuts against the contact Gk and waits in a stationary state. Yes.
The rotating body Jd is rotatably supported around a connection axis CC provided on the door D, and the rotating body J is rotatably supported around a connection axis C provided on the rotating body Jd. A wheel B is mounted on a wheel spindle Ib provided at the tip of the rotating body J. The rotating body J is urged by a pulling spring V in the direction of arrow A in the figure, and the wheel B is moved to the sliding surface K and the door D. It stands still and waits in a state where the sliding surface Kb provided is simultaneously pressed.

The door D rotates about the pivot O in the direction of the arrow B in the figure, and when the wheel Bj attached to the tip of the rotating body Jd comes into contact with the sliding surface Kw provided on the door frame W, the wheel B becomes the sliding surface. After leaving Kb, the sliding surface K is pressed, and the connecting shaft CC is rotated in the direction of arrow B in the figure. The sliding surface K rotates away from the contact Gk, and the push spring U contracts while absorbing the kinetic energy of the door D and decelerating the door D.
16A and 16B, the rotating body J is urged by the pulling spring V in the direction of arrow A in the figure, but the force Fb that the wheel B presses the sliding surface K is shown. The action line is on the opposite side of the pulling spring V across the connection shaft C, and the pressing force Fb rotates the rotating body J about the connection shaft C in the direction opposite to the arrow A in the figure. In FIG. 16 (a), it is made to contact | abut to the contact Gc provided in the door D, and in FIG.16 (b), it is made to contact | abut to the contact Gc provided to the rotary body Jd.

While the door D continues to rotate, the door inertia force becomes “a force by which the sliding surface Kw pushes the wheel Bj back”, and the wheel B presses the sliding surface K. While the wheel B presses the sliding surface K, the sliding surface K continues to rotate with the rotating body J remaining in contact with Gc, but the door D stops and the inertia force of the door disappears. When the sliding surface Kw does not have the force to push the wheel Bj back, and the wheel B does not have the force to press the sliding surface K, the force to prevent the rotating body J from rotating in the direction indicated by the arrow a in FIG. When the rotating body J rotates in the direction indicated by arrow B and the wheel B leaves the sliding surface K, the means for preventing the door D from rotating in the direction indicated by arrow B is released.

Similarly to FIG. 16A, the sliding surface K shown in FIG. 16B also includes a reverse rotation preventing means for preventing the push spring U from restoring. The sliding surface K has a sliding surface KK. The rotating body JJ is urged by the pulling spring Vj, rotates around the support shaft Ij provided on the door D in the direction of the arrow C in the figure, and is mounted on the rotating body JJ. The wheel BB thus moved moves along the sliding surface KK and prevents the sliding surface K from rotating in the direction opposite to the arrow B in the figure.
At the same time as the expansion and contraction of the pressing spring U stops, the restoring of the pressing spring U is prevented and the rotation of the sliding surface K also stops. Although the pressing spring U contracts and stores restoring force, the pressing spring U is restored and the sliding surface K does not rotate in the direction opposite to the arrow B in the figure, and the rotating body Jd is shown in the figure via the wheel B. The door D does not rotate in the opposite direction to the arrow B, and the door D is not returned to the opening direction via the wheel Bj.

If the sliding surface K is not provided with a reverse rotation prevention means for preventing the restoring of the pressing spring U, the restoring of the pressing spring U is started simultaneously with the expansion and contraction of the pressing spring U, and the rotation of the sliding surface K is also started. Even if the door stops and the inertia force of the door disappears, the restoring force stored by the compression of the push spring U is maximum when the door is stopped, and the force Fb that the wheel B presses the sliding surface K is also maximum. Thus, the sliding surface K rotates in the direction opposite to the direction indicated by the arrow A in the drawing while the rotating body J does not come off from the contact Gc, and the door D is rotated in the direction opposite to the direction indicated by the arrow B in the drawing.

When a high-speed rotating door is received and restrained by a spring, the spring expands and contracts to decelerate the door, but eventually the door stops, and the restoring force of the spring starts to return the door. The device shown in FIG. 16 is a speed reducing device that starts moving again without being returned after the door is temporarily stopped. When the door starts moving again, the restoring force of the spring does not act on the door so that the door is fully closed. The door is fully closed with a force that is necessary and sufficient.

When the door is decelerated and stopped, even if the restoring force of the spring remains on the door, if the spring force that rotates the door exceeds the restoring force of the spring, the telescopic spring is further expanded and contracted. The door can start moving again. Even if the door is fully closed by adding a large force that adds the spring's restoring force to the force that is necessary and sufficient to fully close the door, the spring's restoring force is The force required to open the fully-closed door is the minimum force necessary to fully close the door. The apparatus shown in FIG. 16 can be made to start again without returning by applying a force exceeding the restoring force of the spring after the door has stopped.

If the movement when the spring is restored is the same as the movement when expanding and contracting but the direction is reversed, the door is pushed back. The device of FIG. 16 is a one-way operation device in which the operation in the direction in which the push spring U moves while being contracted can be prevented, but the operation in the direction in which the push spring U is restored and pushed back is prevented, and the door is temporarily stopped. Thus, it is a device that releases the resistance that has worked so far so that the movement in the direction of being pushed back is prevented and at the same time it starts moving again. 16 is a device that decelerates the door while pressing the sliding surface K shown in FIG. 16 and contracting the push spring U, and prevents the wheel B and the sliding surface K from separating from each other. In this device, the wheel B and the sliding surface K are separated so that the resistance does not act on the door.

In FIG. 16, before the door is temporarily stopped, the wheel B passes through a route that moves while contacting the sliding surface K, and at the same time as the door stops, the wheel B moves to a route that does not contact the sliding surface K. . The contact point b between the wheel B and the sliding surface K changes the moving direction from the circumferential direction of the circular motion of the door D to the radial direction at the time when the door stops once.
The apparatus shown in FIG. 16 includes a restraining means for restraining the wheel B in a path in contact with the sliding surface K, and a restraining releasing means for separating the wheel B from the sliding surface K. Means for restricting the rotation of the rotating body J and means for releasing the means for restricting the rotation of the rotating body J are provided.

16 (a) and FIG. 16 (b), the rotating body J rotates and the wheel B changes its direction from the revolution track centered on the pivot axis O in the direction perpendicular to the door. Become unaffected.
Even if the restoration of the push spring U is not prevented, the push spring U will not be restored and pushed back by changing the course of the wheel B in the direction perpendicular to the revolution track centered on the pivot axis O. The restraining means of the apparatus is a means for releasing the restraint by pressing and rotating the rotating body J against the Gc by the expansion and contraction of the push spring U by the door inertia force so as not to separate the rotating body J from the contacting Gc. The means is a means for bringing the door D and the sliding surface K away from the state in which the door D and the sliding surface K are relatively integrated via the wheel B. In this case, the restoration of the pressing spring U is prevented, and the “force to hit the rotating body J against the Gc” is released.

When the push spring U starts to expand and contract, even if the door inertia force is maximum, the force of the push spring U is small, and the force that hits the rotating body J against Gc is also small. The rotating body J is free to rotate, and the force for rotating the rotating body J is the force of the tension spring V, and has continued to work since before the pressing spring U began to expand and contract. When the door inertia force is small, the push spring U is little stretched and the force to push back is small. The force that presses the rotating body J against the contact Gc is also small, the rotating body J rotates in the direction away from the contact Gc by the force of the pull spring V, and the door can freely rotate without decelerating the door. When the door inertia force is small, the door deceleration is also small.
When the door inertia force is large, the push spring U is greatly expanded and contracted, and the force of the push spring U is greatly increased. The force that hits the rotating body J and presses it against Gc also increases. The rotating body J is prevented from rotating by the force of the tension spring V.

The push spring U expands and contracts, the force of the push spring U increases, the door inertia force decreases, and the door eventually stops and temporarily stops. Once the door stops, the inertial force of the door disappears, but the force of the push spring U is maximum, and the force that hits the rotating body J and presses against the Gc is maximum, so that the rotating body J does not rotate. If the restoration of the pressing spring U is prevented, the pressing force does not act, and the rotating body J becomes free to rotate. The rotating body J is rotated by the force of the tension spring V. The device shown in FIG. 16 requires a means for preventing the expansion and contraction of the push spring U.

The embodiment of FIG. 16 is prepared in advance so that the force stored in the push spring U is not restored when the door is decelerated, and the door is not rotated in the opening direction by restoring the spring. The moving body B and the sliding surface K are separated by the pulling spring V and the force, and the moving body B is released from the resistance of the push spring U. However, the embodiment of FIG. The force generated is restored and used as a force for pulling away from the moving body that moves relatively integrally with the moving body. At the same time as the door is stopped, FIG. Also in b), the rotating body JJ rotates and the wheel B and the sliding surface K are separated. The moving body B moves freely. The door does not open and begins to close.

The moving body and the moving body are the moving body and the moving body defined in FIG. 5, and are the moving body D and the moving body S in FIG. In FIG. 17B, a rack D and a ratchet gear B are shown.
17A, the moving body B and the sliding surface K are relatively integrated with each other through the contact b, and the push spring U expands and contracts while moving in the same direction. In FIG. The linear motion of D is converted into the rotation of the ratchet gear B, and the tension spring V expands and contracts.

FIG. 17 (a1) shows a state in which the wheel B is in contact with the sliding surface Kd of the moving body D, and FIG. 17 (a2) shows the moving body D moving in the direction of the arrow B in the drawing along the track Zm. Then, the wheel B moves along the sliding surface Kd in the direction of arrow A in the figure, the moving body S moves along the track Zm in the direction of arrow B in the figure, and the push spring U expands and contracts to move the moving body. D shows the state of deceleration. FIG. 17 (a3) shows that after the stop, the rotating body JJ rotates around the fixed support shaft Sw in the direction indicated by the arrow C so that the wheel B moves away from the moving body D and the pushing spring U does not push the moving body S back. This shows the state.

In FIG. 17A, the link A is rotatably supported around a connection axis C provided on the moving body S. The link A is provided with a wheel B at the tip, and the link Ag is rotatably supported around a support shaft Ia provided at an intermediate portion of the link A. The rotating body J that is rotatably supported around the connecting shaft C is provided with ratchet teeth Rj at the outer edge, and a ratchet claw Ra is provided at the tip of the link Ag. The ratchet pawl Ra meshes with the ratchet teeth Rj, and comes into contact with and disengages.
As shown in FIG. 17 (a1), before the moving body D comes into contact with the wheel B, the rotating body J is urged by the push spring Uj and hits Gj to be stationary. The link A is urged by the push spring Ua and presses the rotating body J via the ratchet pawl Ra to be stationary.

17 (a1) and 17 (a2), the sliding surface Kd presses the wheel B by the dynamic inertia force of the moving body D. The link A rotates in the direction of the arrow D in the figure, the wheel B moves, and the action line of the force Fb that the sliding surface Kd presses the wheel B also moves, but the action line of the pressing force Fb is from the fixed support shaft Sw. At the contact Gjj side, the rotating body JJ presses Gjj and stops, and the push spring U contracts. At the same time, the ratchet pawl Ra moves along the outer edge of the rotating body J in a direction away from the start end Rjs.

As shown in FIG. 17 (a2), when the wheel B rotates around the corner portion Kde of the sliding surface Kd, the line of action of the pressing force Fb hits the fixed support shaft Sw and becomes opposite to Gjj. The rotating body JJ rotates in the direction opposite to the arrow C in the figure. The contact Ga is a position where the line of action of the pressing force Fb crosses the fixed support shaft Sw, and restricts the rotation of the link A in the direction of the arrow in the figure. After the link A hits the contact Ga, the push spring U only contracts.

The check valve Gs is rotatably supported around a support shaft Is provided on the moving body S, and is urged by a push spring Us to press the groove M side surface. As shown in FIG. 17 (a2), the force pressing the side surface of the groove M does not increase when the moving body S advances in the direction indicated by the arrow B in the figure. However, as shown in FIG. When returning in the direction opposite to the middle arrow B, the check valve Gs rotates in the direction indicated by the arrow E in the figure to increase greatly, and the moving body S stops without returning in the direction opposite to the arrow B in the figure. The force with which the wheel B presses the sliding surface Kd is lost.
When the moving body D is fully decelerated and the pressing spring U is fully contracted, the force that pushes back the moving body S is maximized. However, when both the moving body S and the moving body D stop, the sliding surface Kd presses the wheel B. Since the force is also lost, the wheel B can move with the restoring force of the compressed push spring Ua.

The rotation of the link A in the direction opposite to the arrow D in the drawing is prevented by the ratchet pawl Ra meshing with the ratchet teeth Rj. Due to the restoring force of the pressing spring Ua, the tip bb of the rotating body J presses the sliding surface K provided on the fixed portion W, and the rotating body JJ rotates in the direction of arrow C in the figure. The tip end bb is located farther from the connection axis C than the wheel B, and moves the wheel B in the direction of arrow A in the figure while moving along the sliding surface K. The wheel B leaves the sliding surface Kd and goes out of the path of the moving body D.

FIG. 17 (b1) shows a state in which the rack D is in contact with the ratchet gear B, and FIG. 17 (b2) shows that the linear motion of the rack D is converted into the rotation of the ratchet gear B in the direction indicated by the arrow a in FIG. FIG. 17 (b3) shows the state in which the tension spring V expands and contracts. After stopping, the rotating body JJ rotates in the direction of the arrow around the fixed support shaft Sw, the wheel B moves away from the moving body D, and the pushing spring U moves. A state where the body S is not pushed is shown.

In FIG. 17A, a rotating body J is rotatably supported around a connection axis C provided on the rotating body JJ. A ratchet claw Ra is attached to the support shaft Ia provided at the tip of the rotating body J, and the ratchet claw Ra moves along the ratchet teeth Rj provided at the outer edge of the ratchet gear B. The ratchet pawl Ra allows the ratchet gear B to rotate in the direction of arrow A in the figure and prevents reverse rotation.
FIG. 17 (b3) is a state diagram when the rack D is stopped and the tension spring V is restored, and the ratchet gear B is opposite to the arrow a in the figure by the restoring force of the tension spring V, and the ratchet pawl Ra is the ratchet tooth. A state in which the rotating body J is engaged with Rj and rotates in the direction of arrow C in the figure is shown. The state where the tip of the rotating body J presses the rack D, the rotating body JJ rotates about the fixed support shaft Sw, and the ratchet gear B is separated from the rack D is shown.

When the rack D completely decelerates and stops, the force by which the ratchet gear B pushes back the rack D is maximized. However, the ratchet gear B is separated from the rack D at the same time as the pulling spring V starts to recover and the ratchet gear B rotates. The tension spring V is not restored and the rack D is not returned. In FIG. 17A, the moving body S is prevented from returning and the push spring Ua is not restored. However, in FIG. 17B, the restoration of the tension spring V is not inhibited, and the rack D is decelerated. At the same time, and at the same time, it is made not to decelerate by the restoring force of the tension spring V.

FIG. 17C is an explanatory diagram of a one-way clutch that drives only in one direction and idles in the reverse direction. Like the ratchet mechanism in FIGS. 17A and 17B, the operation direction is limited to one. To do. A support shaft I is equally distributed on a circle Ro of a disk PL that rotates about the pivot O, and a cam body B whose outer periphery is a vortex is mounted on the support shaft I. The movable body K has a sliding surface K and moves along the sliding surface KK. The sliding surface KK is pivotally supported around a fixed support shaft Sw provided on the fixed portion W and attached to the push spring U. The cam body B is pressed by being urged. It is assumed that the frictional force is small between the sliding surface K and the sliding surface KK.
FIG. 17 (c1) shows a state where the disk PL rotates clockwise and the moving body K does not move. FIG. 17 (c2) shows a state where the disk PL rotates counterclockwise and the moving body K slides. The state which moves in the direction away from the contact Gk provided in KK is shown.

The cam body B comes into contact with the sliding surface K at the contact b, and in FIG. 17 (c1), the cam body B rotates counterclockwise around the support shaft I, and the distance between the contact b and the support shaft I decreases. . The friction between the cam body B and the sliding surface K decreases. In FIG. 17 (c2), the cam body B rotates around the support shaft I in the clockwise direction. As the contact b moves along the outer edge of the cam body B, the distance between the contact b and the support shaft I is increased, so that the cam body B presses the sliding surface K by the wedge effect. The friction between the cam body B and the sliding surface K increases, and the rotation of the disk PL is converted into a linear motion of the moving body K. As shown in FIG. 17 (c2), the movable body K is driven only in the direction of arrow A in the figure.

Also in the apparatus of FIG. 17 (c), a spring V (not shown) is attached around the support shaft I. When the disk PL rotates clockwise in FIG. 17 (c1), the spring V (not shown) is rotated around the support shaft I. The spring V (not shown) is restored and the disk PL is rotated counterclockwise.
In the apparatus of FIGS. 17A and 17B provided with a ratchet mechanism, the rotating body J does not rotate around the connecting shaft C when the spring tension spring V expands and contracts, but rotates when the spring is restored. Also in the apparatus of FIG. 17C equipped with a one-way clutch, the sliding surface K does not move when the spring V is expanded and contracted, but moves when the spring is restored.

The ratchet gear B and the rotating body J in FIG. 17B are replaced with the disk PL and the sliding surface K in FIG. 17C, and the ratchet gear B in FIG. 17B is replaced with the disk PL in FIG. Then, assuming that the rotating body J in FIG. 17B is the sliding surface K in FIG. 17C, the cam body B attached to the disk PL in FIG. If it moves along the rack D, when the disk PL is rotated by the movement of the rack D and the spring expands and contracts, the sliding surface K in FIG. 17C does not move, the spring is restored and the disk PL is reversed. The sliding surface K is moved by rotating. When the sliding surface K moves and pushes the rack D when the spring is restored, the rotating body J shown in FIG.

In FIG. 17B, the ratchet gear Bg does not transmit the rotation to the rotating body J when the spring expands and contracts. The rotation is transmitted to the rotating body J when the spring is restored. In FIG. 17C, the disk PL rotates clockwise and the moving body K does not move. The moving body K moves by rotating counterclockwise.
The ratchet mechanism in which the ratchet gear B transmits the rotation to the rotating body J in FIG. 17B and the one-way clutch mechanism in which the rotation of the disk PL is converted into the movement of the sliding surface K in FIG. This is a mechanism that drives only in one direction when the movement is transmitted to the driven side, and drives only in one direction during restoration even if a spring is attached to the driving side and the moving body reciprocates.

However, when a spring is attached to the driven side, the drive side operation is transferred to the driven side operation, the spring expands and contracts, and when the spring is restored and the driven side operates in the reverse direction, the drive side also operates in the reverse direction.
In FIG. 17B, the ratchet gear B rotates and the spring that has expanded and contracted is restored, and the ratchet gear reversely rotates to return the rack D. The ratchet gear B rotates and reverses in the reciprocating motion of the rack D.
In FIG. 17C, if a moving body (not shown) rotates the disk PL to expand and contract a spring V (not shown), the spring V is restored and the disk PL reversely rotates to return the moving body (not shown). To exercise. If a moving body (not shown) reciprocates, the disk PL rotates and reversely rotates. When a spring is attached to the one-way clutch mechanism so that the one-way clutch follows the moving body and the spring expands and contracts, when the spring is restored and the one-way clutch returns, the moving body also returns.

When a spring is attached to the one-way clutch, the function of operating in only one direction is lost. Simply attaching a spring to the one-way clutch absorbs the dynamic inertia force of the door with the expansion and contraction of the spring, and after the door is decelerated and temporarily stopped, when the spring is restored, it does not begin to rotate in the direction to open the door. You can't do that.
For example, when the spring is not attached to the disk PL in FIG. 17 (c2), if the sliding surface K moves forward and the disk PL is driven, the sliding surface K moves backward and the disk PL is idled. When the spring is attached to the disk PL, when the sliding surface K moves backward, the disk PL moves backward without idling.

Figure 18 shows the one-way clutch attached with a spring, which absorbs the dynamic inertia of the door by the expansion and contraction of the spring. When the spring is restored after the one-way clutch is rotated by the door and the spring expands and contracts, the one-way clutch runs idle and pushes the door back without leaving the one-way clutch and the door. It is explanatory drawing of the mechanism made not to exist.

The one-way clutch shown in FIG. 18 (a) is substantially the same as the one-way clutch shown in FIG. 17 (c), but the cam body B shown in FIG. 18 (a) has a pivot axis O in the vicinity of the outer edge of the disk PL. It is mounted on a spindle I that is equally distributed at the same distance, and includes a “part where the outer periphery is a vortex” and a “part where the outer periphery is a circumference”. A circumferential sliding surface Ko is provided on the fixed portion W, and the sliding surface Kd provided on the moving body D and the sliding surface Ko face each other with the cam body B interposed therebetween.
The sliding surface Ko keeps contact with the “part whose outer periphery is a circumference”, and the number of cam bodies B sandwiched between the sliding surface Kd and the sliding surface Ko is limited to one or two, and the other The cam body contacts the sliding surface Ko but does not contact the sliding surface Kd.

The “portion where the outer periphery is a circumference” of the cam body B moves and rotates along the sliding surface Ko, and the cam body B swings between the standing state and the lying state. On both sides of each cam body, there is provided a hit (not shown) in which the cam body B is stationary in the standing state and the lying state. When the cam body B stands up and stops, it is supported by a spring so that the cam body B can continue to rotate slightly even after the cam body B comes into contact.
The standing state is a state where it reaches a position sandwiched between the sliding surface Kd and the sliding surface Ko and stands by so as to come into contact with the sliding surface Kd, and the lying state is a state between the sliding surface Kd and the sliding surface Ko. It is in a state of waiting so as not to come into contact with the sliding surface Kd by reaching the position between them. The cam bodies around the one or two cam bodies stand by in a standing state or a lying state, reach a position sandwiched between the sliding surface Kd and the sliding surface Ko, and come into contact with the sliding surface Kd. Or do not touch.

As shown in FIG. 18 (a1), the cam body in which the sliding surface Ko and the portion where the outer periphery is a circle is in contact, the disk PL rotates around the pivot O in the direction of the arrow a in the drawing as shown in FIG. Then, it rotates and stands in the direction of arrow C in the figure. The “part where the outer periphery is a vortex line” of the cam body B protrudes outside the disk PL. Further, as shown in FIG. 18 (a2), when the spring is restored, the disk PL rotates in the direction opposite to the arrow A in the figure, and rotates and falls in the direction opposite to the arrow C in the figure. The “part where the outer periphery is a vortex” of the cam body B is accommodated in the disk PL.

At the time of expansion and contraction of the spring, as shown in FIG. 18 (a1), the moving body D moves in the direction of the arrow B in the figure, and the “portion where the outer periphery is a vortex line” along the sliding surface Kd. When moved, the “portion where the outer periphery is a circle” of the cam body B further rotates further in the direction of the arrow C in the figure, and the “contact portion of the cam body B is a spiral line” and the sliding surface K door. The distance between b and the spindle I increases. The force with which the cam body B presses the sliding surface Kd increases, and the disk PL rotates in the direction of the arrow a in the figure. The tension spring V is stretched, and the moving body D decelerates.
At this time, the rotation direction of the “portion where the outer periphery is a circumference” moving along the sliding surface Ko is also in the direction of the arrow C in the figure, and the “portion where the outer periphery is a vortex” is along the sliding surface Kd. It is the same as the direction of movement and rotation.

At the same time as the moving body D decelerates and stops, as shown in FIG. 18 (a2), the stretched spring V is restored, and the disk PL rotates in the direction opposite to the arrow A in the figure.
At the moment when the tension spring V is restored and the disk PL rotates in the direction opposite to the arrow A in the figure, one of the cam bodies B is in contact with the sliding surface Kd. The cam body B rotates along the sliding surface Kd in the direction of the arrow C in the figure, and simultaneously moves along the sliding surface Ko and rotates in the direction opposite to the arrow C in the figure. However, during a short period of rotation in the direction opposite to the arrow A in the figure, the moving body D is moved slightly in the direction opposite to the arrow B in the figure without rotating, and immediately leaves the sliding surface Kd.

The other cam body B is such that the “portion whose outer periphery is a circle” moves along the sliding surface Ko and rotates in the direction opposite to the arrow C in the figure, so that the cam body B is separated from the sliding surface Kd. Become. When one of the cam bodies B moves away from the sliding surface Kd, the other does not come into contact with the sliding surface Kd, so that the moving body D does not move more than a little.
Even if the cam body moves along the sliding surface Ko and the sliding surface Kd at the same time, the rotation direction of the “portion where the outer periphery is a circumference” moving along the sliding surface Ko and “the outer periphery is a vortex line” The direction in which the “part” moves along the sliding surface Kd and rotates is the same when the spring expands and contracts, and the cam body rotates, but when the spring is restored, the directions are opposite to each other. Does not rotate. If the force that causes the sliding surface Kd to rotate one of the cam bodies B in the direction of the arrow C in the figure is stronger than the force that the sliding surface Ko rotates in the direction opposite to the arrow C in the figure, the cam body B slides. The moving body D moves in the direction opposite to the arrow B in the figure until it moves away from the surface Kd.

Considering the moving body D that moves in the direction of arrow B in the figure as the door D that rotates and closes, when the “part where the outer periphery is a vortex” moves along the sliding surface Kd, the door D Extends the pulling spring V, decelerates and stops. At the same time, the door D is slightly returned in the opening direction, but is released from the decelerator of FIG.
The speed reducer in FIG. 18 (a) does not move to a position where it does not come into contact with the door as the entire apparatus moves greatly like the speed reducer in FIG. 17 (a), but the cam body B inside the apparatus rotates. The device itself does not move.

As the door is decelerated, the force with which the spring V pulls back the door increases, and the force with which one of the cam bodies B rotates in the direction of the arrow C in the drawing and presses the sliding surface Kd increases. As the spring V expands and contracts, the door is decelerated, and as the force pressing the sliding surface Kd increases, the frictional force acting between the sliding surface K and the sliding surface Kd increases and the door is decelerated. .
However, even if the force that presses the sliding surface Kd increases and the frictional force acting between one of the cam bodies B and the sliding surface Kd increases, the force of the spring V that reversely rotates the disk PL. Will increase. If the frictional force is less than the force of the spring V, one of the cam bodies B starts to move while sliding along the sliding surface Kd even when the door continues to close and rotate, and the disk PL rotates in the reverse direction.
When one of the cam bodies B revolves around the pivot axis O, the spring is restored away from the sliding surface Kd, and the reduction gear of FIG. Since one of the cam bodies B falls down and passes through a position away from the sliding surface Kd, even when one of the cam bodies B moves away from the sliding surface Kd, the door continues to rotate and close. The spring will restore the door without slowing down.

Even if the force of the spring V increases, the frictional force acting between the cam body B and the sliding surface Kd increases, and the spring continues to expand and contract without being restored while no slip occurs. When the door comes to a stop without slipping, the force with which the pull spring V pulls the door back is maximum. One of the cam bodies B revolves around the pivot axis O while pulling back the door without slipping, and the cam body B moves away from the sliding surface Kd.

FIG. 18 (b) transmits the linear motion of the moving body D to the linear motion instead of the rotation of the moving body. The moving body D moves along the track Zm provided in the fixed portion W, and the moving body S is the moving body. It moves along the sliding surface Ko provided in the fixed part W in parallel with D.
The cam body B shown in FIG. 18A is attached to the moving body S, and the sliding surface Kd provided on the moving body D and the sliding surface Ko face each other with the cam body B interposed therebetween. The sliding surface Ko is urged by the pressing spring Uk, and presses the “portion where the outer periphery is a circumference” of the cam body B so as to always keep contact.

As shown in FIG. 18 (b1), before the moving body D moves in the direction of arrow B in the figure and the “portion where the outer periphery is a vortex” moves along the sliding surface Kd, The cam body B is on standby so that the “portion where the outer periphery is a vortex” moves along the sliding surface Kd.
As shown in FIG. 18 (b1), when the moving body D moves in the direction of the arrow B in the figure, the “portion where the outer periphery is a vortex line” moves along the sliding surface Kd. Rotating in the direction C, the force that the “outer part of the cam body B is a vortex line” presses the sliding surface Kd increases, and the moving body D and the moving body S become relatively integrated, and the direction of arrow B in the figure. Move to. The tension spring V is stretched.
When all of the kinetic energy of the moving body D is converted into the strain energy of the pulling spring V, the moving body D has no force to move in the direction of arrow B in the figure, and conversely, the force to pull back the moving body S is maximized.

As shown in FIG. 18 (b2), the extended tension spring V contracts, and the moving body S moves in the direction of arrow A in the figure, but at the moment the moving body S moves in the direction of arrow A in the figure, The cam body B is in contact with the sliding surface Kd and the sliding surface Ko. Although the sliding surface Ko does not move, the sliding surface Kd moves in the direction of arrow A in the figure, and the cam body B does not move relative to the sliding surface Kd. The cam body B rotates in the direction indicated by the arrow D in the figure, and the distance between the contact point b between the cam body B and the sliding surface Kd and the support shaft I decreases and moves away from the sliding surface Kd. Thereafter, the moving body D does not move.

As shown in FIG. 18 (b2), the extended tension spring V contracts, and the moving body S moves in the direction of arrow A in the figure, but at the moment the moving body S moves in the direction of arrow A in the figure, The cam body B is in contact with the sliding surface Kd and the sliding surface Ko. Although the sliding surface Ko does not move, the sliding surface Kd moves in the direction of arrow A in the figure, and the cam body B does not move relative to the sliding surface Kd. The cam body B rotates in the direction indicated by the arrow D in the figure, and the distance between the contact point b between the cam body B and the sliding surface Kd and the support shaft I decreases and moves away from the sliding surface Kd. Thereafter, the moving body D does not move.

Also in FIG. 18 (b), as in FIG. 18 (a), the force of the tension spring V increases at the same time, and the cam body B in the figure increases as the moving body D continues to move in the direction of arrow B in the figure. Rotating in the direction of arrow C, the force with which the cam body B presses the sliding surface Kd increases. The greater the force with which the cam body B presses the sliding surface Kd, the greater the frictional force between the cam body B and the sliding surface Kd, and the cam body B slides along the sliding surface Kd while the arrow in the figure. Resist not to move in the direction b.

Whether the cam body B starts to slide along the sliding surface Kd depends on the frictional force acting between the cam body B and the sliding surface Kd and the force with which the pulling spring V pulls the moving body S back in the direction of arrow A in the figure. If the frictional force is smaller than the pulling back force, slipping occurs. Even if slipping occurs, the cam body B does not rotate but moves in the direction of arrow A in the figure along the sliding surface Kd. At the same time, the tension spring V contracts and the force of the tension spring V decreases. From the position where the tension spring V can no longer pull back the cam body, there is no slip, and the cam body B further rotates in the direction of the arrow C in the figure, and approaches the moving body D along the sliding surface Kd. Start moving in the direction of the middle arrow b. The tension spring V is stretched and the door deceleration is resumed.

FIG. 18C shows a general cam type one-way clutch to which “an arcuate sliding surface Ko provided on the fixed portion W” shown in FIG. 18A is attached.
The cam body B shown in FIG. 18 (c) is mounted on a support shaft I that is equally distributed to the outer ring PL at the same distance from the pivot axis O. A portion that is a circumference ”. The “part where the outer periphery is a vortex” is biased by a spring (not shown), presses the outer periphery of the inner ring PO, and slides along the outer periphery of the inner ring PO. The “part whose outer periphery is a circumference” slides along the circumferential sliding surface Ko.

The sliding surface K is provided on the fixed portion W, and the rack D moves along the sliding surface K and the outer edge portion of the outer ring PL. The outer ring PL is a pinion that moves along the rack D.
18A and 18B, the cam body B presses the sliding surface Kd, and the sliding surface Kd moves along the sliding surface K. The greater the force with which the cam body B presses the sliding surface Kd, the greater the frictional force between the sliding surface Kd and the sliding surface K, resisting the movement of the sliding surface Kd. In FIG. 18C, no frictional force acts between the sliding surface Kd and the sliding surface K. The sliding surface Kd moves without resistance.

In FIG. 18 (c1), when the inner ring PO rotates in the direction of the arrow A in the figure, the cam body B rotates in the direction of the arrow C in the figure, and the contact surface pressure between the cam surface and the inner ring PO increases, resulting in resistance. Transmits power to the outer ring PL. The outer ring PL rotates in the direction of arrow A in the figure, and the sliding surface Kd provided on the rack D moves in the direction of arrow B in the figure to contract the push spring U.
18 (c), unlike FIGS. 18 (a) and 18 (b), the cam body B does not press the moving body D in one direction, but the inner ring PO has the same size from multiple directions. The rotating shaft of the inner ring PO does not move. Slip does not occur due to the wedge effect acting between the cam surface and the contact surface of the inner ring PO. Therefore, the spring continues to expand and contract until the door stops.

In FIG. 18 (c2), the compressed pressing spring U is restored, the sliding surface Kd moves in the direction opposite to the arrow B in the figure, and the outer ring PL rotates in the direction opposite to the arrow A in the figure. The cam body B slides along the sliding surface Ko and rotates in the direction opposite to the arrow C in the figure. The contact surface pressure between the cam surface and the inner ring PO is lowered, and the power transmission is cut off by sliding.
At the moment when the outer ring PL starts to rotate in the direction opposite to the arrow a in the figure, the cam body moves along the sliding surface Ko and the outer periphery of the inner ring PO simultaneously. The direction of rotation of the “portion where the outer periphery is a circle” moving along the sliding surface Ko and the direction of rotation of the “portion where the outer periphery is a vortex” along the outer periphery of the inner ring PO are the directions of the spring When restoring, the cam bodies are in opposite directions and the cam body does not rotate.

18 (a) and 18 (b), when the cam body B moves along the sliding surface Ko and the sliding surface Kd at the same time, the cam body B in FIG. When the spring moves, the sliding surface Ko and the sliding surface Kd move in directions opposite to each other at the same time. The moving surface Kd moves in the same direction, and the cam body B receives forces in opposite directions from the sliding surfaces on both sides, and moves while sliding on both sliding surfaces without rotating.
18 (a) and 18 (b), if the moving body has stopped or continues to advance, if the inner ring PO stops rotating or continues to rotate in FIG. 18 (c), the spring is restored. Thus, the cam body B rotates in the direction of the arrow C in the figure and does not rotate in the direction opposite to C.

18 (a) and 18 (b), the cam body B is in an unrotatable state at the moment when it is separated from the sliding surface Kd of the moving body D and the inner ring PO in FIG. 18 (c). However, if the moving body is returning in FIGS. 18A and 18B, the cam body B can rotate in the direction opposite to the arrow C in the figure.
In FIG. 18 (c), the cam body B can rotate in the direction opposite to the arrow C in the figure if the inner ring PO rotates in the reverse direction. Although the moving body is pushed back by the spring, when the cam body B is rotated slightly backward by being pushed back slightly, the moving body is released from the restoring force of the spring. That is, the moving body can no longer continue to move and stops, and at the moment when it is pushed back slightly, it is not pushed back by the spring.

If the sliding surface Ko is an internal gear and the "portion where the outer periphery is a circumference" of the cam body B is a pinion that meshes with the internal gear and moves, then the sliding surface Ko shows the cam body B. The force to rotate in the direction opposite to the middle arrow C becomes stronger than the force that the outer periphery of the inner ring PO rotates the cam body B in the direction of the arrow C in the sliding surface view, and the cam body B is opposite to the arrow C in the figure. Rotate in the direction. The inner ring PO does not need to assist the reverse rotation of the cam body B by rotating in the direction opposite to the arrow a in the figure, and even if the rotation of the inner ring PO is stopped or prevented, the cam body B rotates in reverse and the power Disconnect the transmission.

The cam body B is only slightly rotated or reversely rotated when the inner ring PO starts to rotate slightly in the direction of arrow A in the figure and when the outer ring PL starts to rotate slightly in the direction opposite to arrow A in the figure. After a slight rotation or reverse rotation, it remains stationary. In order to rotate slightly or reversely, only one tooth needs to be attached to the “part where the outer periphery is a circumference” of the cam body B and mesh with the internal gear Ko. The cam body B cannot be kept stationary without rotating or reversely rotating without being engaged.

A reverse rotation prevention device using a ratchet (not shown) is attached to the sliding surface Ko in FIG. 18C, and the rotation of the sliding surface Ko only in the direction opposite to the arrow a in the drawing is stopped by the reverse rotation prevention device (not shown). .
At the time of expansion and contraction of the spring shown in FIG. 18 (c1), the sliding surface Ko is free to rotate in the direction of the arrow a in FIG. 18 and is attached to the “part whose outer periphery is a circumference” as shown in FIG. 18 (c3). The single gear Gb revolves around the pivot axis O while meshing with the internal gear of the sliding surface Ko, and the sliding surface Ko also rotates together with the outer ring PL.

When the spring shown in FIG. 18 (c2) is restored, the sliding surface Ko is stopped from rotating in the direction opposite to the arrow a in the figure. At the moment when the outer ring PL starts to reversely rotate, with the single gear Gb meshing with the inner gear Ko of the sliding surface Ko, the outer ring PL rotates reversely and the single gear Gb rotates on the sliding surface Ko. Rotating along the internal gear Ko, the cam body B is rotated in the direction opposite to the arrow C in the figure. Thereafter, as shown in FIG. 18 (c4), the single gear Gb remains disengaged without meshing with the internal gear Ko, and the cam body B stops without continuing reverse rotation and moves along the internal gear Ko. .
When the outer ring PL rotates in the direction of arrow A in the figure, the single gear Gb meshes with the internal gear Ko by the spring V.

A door inertia force and a “biasing force for closing and rotating the door” act on the door. In FIGS. 17 and 18, when the door starts to recover and the door is stationary, when the door inertia force is applied, the spring is restored by the restoring force of the spring. Is pulled back. If the door inertia force does not work, for example, if the door moves only with the urging force that closes and rotates the door, and the spring is extended and contracted, the door is where the restoring force of the spring balances the urging force that rotates the door. Is stationary. Except in the case of FIG. 16, if there is no force to start the operation of preventing the restoring force of the spring from acting on the door, the door does not start again. In particular, if the door does not begin to rotate in the opening direction, the door will not start again if there is no force to start the operation that prevents the restoring force of the spring from acting on the door.

In order to start the operation of preventing the restoring force of the spring from acting on the door, the restoring force of the expanded and contracted spring must be greater than the urging force for closing and rotating the door at the position where the door is stopped.
When door inertia force is applied to the door, when the door is decelerated and stopped, the restoring force of the spring is greater than the urging force that causes the door to close and rotate by the amount of expansion and contraction due to the door inertia force. Starts the action that prevents the force from acting on the door.
FIG. 19 shows a state in which the spring is expanded and contracted in advance, and when the speed reducer of FIG. 19 starts to act on the door, the “spring that has been expanded and contracted more than the biasing force for closing and rotating the door” begins to expand and contract. When there is no door inertia force on the door, when the door tries to expand and contract the spring, the spring is restored without starting to expand and contract, and the "operation to prevent the spring restoring force from acting on the door" starts. .

FIG. 19 (a) prevents the spring from starting to expand and contract with respect to the door that moves at a low speed only by “the urging force for closing and rotating the door”, and FIG. 19 (b) illustrates that the door is a spring. Even if it starts to expand and contract, the spring that has been expanded and contracted in advance is restored, and the “operation for preventing the restoring force of the spring from acting on the door” is started.
In FIG. 19A, the moving body D and the moving body S move along a track Zm provided in the fixed portion W, and the moving body S is provided with two support shafts I. Each support shaft I has an outer periphery. The cam body B and the cam body BB, which are vortex lines, are attached, and the cam body B moves along the side surface of the moving body D. The cam body BB is “sliding provided on the fixed portion W in parallel with the track Zm. It moves along the “moving surface Ko”.

The sliding surface Ko does not move in the direction along the track Zm, but moves in the direction perpendicular to the track Zm. It is urged by the pressing spring Uk and presses the cam body BB so that the contact is always maintained. The cam body BB rotates to change the distance between the "contact point bb between the cam body BB and the sliding surface Ko" and the support shaft I. The sliding surface Ko and the support shaft I are changed according to the change in the distance. The distance between and changes.
The sliding surface Ko and the “part where the outer periphery is a vortex” of the cam body BB are serrated, and the saw blade allows the cam body BB to move in the direction of the arrow B in the figure without rotating. The cam body BB is rotated when moving in the direction opposite to the middle arrow b.

FIG. 19A1 shows a standby state before the moving body D contacts the moving body S. FIG. A “force that moves the moving body D in the direction of the arrow B in the figure” acts on the moving body D by urging means (not shown). A force greater than the “force for moving the moving body D in the direction indicated by the arrow B” acts on the moving body S in the direction opposite to the arrow B in the figure by the push spring U. The moving body S is supported by wheels Ba.

The wheel Ba is mounted on a support shaft Ij provided at the tip of the rotating body J, and the rotating body J is rotatably supported around a fixed support shaft Sw provided on the fixed portion W and is urged by a spring Vj. Hit Gj and stop.
FIG. 19 (a2) shows a state in which the moving body D moves in the direction of the arrow B in the figure, the wheel Ba moves along the side surface Kd of the moving body D, and the rotating body J hits and separates from Gj. At the same time, the wheel Ba moves along the sliding surface Ks provided on the moving body S.

The action line of the force Fj that the sliding surface Ks presses the wheel Ba is on the opposite side of Gj with the fixed support shaft Sw in between, and the rotating body J is in the direction of the arrow D in the figure with the fixed support shaft Sw as the axis. Rotate to. The moving body S is moved by the push spring U in the direction opposite to the arrow B in the figure, and the cam body BB moves along the sliding surface Ko and rotates in the direction of the arrow C in the figure. The cam body B rotates with the rotation of the cam body BB, and moves to a place where it does not contact the moving body side surface Kd. FIG. 19A2 is a state diagram when the moving body D moves at a low speed, and the moving body D continues to move without contacting the cam body B. FIG.

FIG. 19 (a3) is a state diagram when the moving body D moves at a high speed. The moving body D contacts the cam body B before moving to a place where the cam body B does not contact the moving body side surface Kd. Show. The cam body B moves along the moving body side surface Kd and rotates in the direction of the arrow C in the figure, so that the moving body D and the moving body S are relatively integrated.
FIG. 19 (a4) is a state diagram when the moving body D and the moving body S continue to move in the direction indicated by the arrow B in FIG. If the force that pushes back the moving body S in the direction opposite to the arrow B in the figure and the force of the biasing means (not shown) that moves the moving body D in the direction indicated by the arrow B in the figure, the moving body D and the moving body S also stop. In order to move the moving body D further in the direction of the arrow B in the figure, a large force for further contracting the push spring U is required.

At the stage where the moving body D and the moving body S shown in FIG. When the force is more than “force” and once stopped as shown in FIG. 19 (a4), the push spring U is further contracted, so that the moving body D and the moving body S are pushed back in the direction opposite to the arrow B in the figure. Become.
The cam body BB moves along the sliding surface Ko and rotates in the direction opposite to the arrow C in the figure, and the cam body B also rotates in the direction opposite to the arrow C in the figure to leave the moving body side surface Kd. The moving body D does not move, only the moving body S moves in the direction opposite to the arrow B in the figure, and the push spring U is restored.
When the moving body D moves in the direction opposite to the arrow B in the figure and moves away from the moving body S, the apparatus returns to the initial state shown in FIG. 19 (a1).

In the cam body shown in FIG. 18, one cam body is provided with “a portion where the outer periphery is a vortex” and “a portion where the outer periphery is a circumference”.
In FIG. 19, two cam bodies are rotatably supported around a common support shaft I. Each of the two cam bodies has a vortex line on the outer periphery, and is a cam body B that contacts or leaves the moving body D and a cam body BB that contacts or leaves the sliding surface Ko.

In FIG. 18, if only the moving body is returned while the moving body is stopped when the spring is restored, the cam body B moves along the sliding surface Ko and the sliding surface Kd at the same time. B receives forces in opposite directions from the sliding surfaces on both sides, and moves while sliding on the sliding surfaces on both sides without rotating. When there is no slip, both the moving body and the moving body are reversed, and the moving body is reversed at the double speed of the moving body, the cam body is rotated and the moving body and the moving body are separated.
Although the same can be said in FIG. 19, both of the two cam bodies do not move while sliding, but only the cam body BB rotates even when the cam body B slides. When the moving body stops and the cam body B slides while the spring is restored, only the moving body moves backward and only the cam body BB rotates.

FIG. 19 (b) shows a general cam-type one-way clutch similar to FIG. 18 (c) to which “an arcuate sliding surface Ko provided on the fixed portion W” is attached. With the pivot O as the rotation axis, the rotation in the range of (ii) of the door is transmitted to the inner ring PO that rotates in the direction of arrow B in the figure, the outer ring PL that rotates along the outer edge of the inner ring PO, and the outer ring PL Fixes the support shaft I equally spaced from the pivot axis O, two cam bodies B and BB that are rotatably supported around the support shaft I, and one mounting shaft. And a spring V that is fixedly supported by the portion W and movably supports the other mounting shaft on the outer ring PL. As shown in FIG. 19 (b1), the spring V expands and contracts when the outer ring PL rotates in the direction indicated by the arrow B in the figure, and as shown in FIG. Rotate in the opposite direction.

As shown in FIG. 19 (b1), the cam body B is urged by a spring (not shown), presses the outer periphery of the inner ring PO, and slides along the outer periphery of the inner ring PO. When the inner ring PO rotates in the direction indicated by the arrow B in the figure, the distance between the “contact b with the outer periphery of the inner ring PO” and the support shaft I increases in the “portion where the outer periphery is a vortex”. The outer ring PL is rotated in the direction indicated by the arrow B in the figure.
The cam body BB is biased by a spring (not shown), presses the inner circumferential portion of the sliding surface Ko, and slides along the sliding surface Ko. When the inner ring PO rotates in the direction of the arrow B in the figure, even if the “portion where the outer periphery is a vortex line” contacts the sliding surface Ko, the cam body BB is in contact with the contact bb with the sliding surface Ko. It rotates in the direction in which the distance from the support shaft I decreases (in the direction of arrow C in the figure) and does not resist the rotation of the outer ring PL in the direction of arrow B in the figure.

As shown in FIG. 19 (b2), when the spring V is restored and the outer ring PL rotates in the direction of the arrow A in the figure, the cam body BB rotates in the direction opposite to the arrow C in the figure, The distance between the "part where the outer periphery is a vortex" and the contact point bb between the sliding surface Ko and the support shaft I increases. The contact Gbb provided on the cam body BB contacts the contact Gb provided on the cam body B, and the cam body B is rotated in the direction opposite to the arrow C in the figure so that the cam body B is separated from the outer peripheral portion of the inner ring PO. To do.

In the case of FIG. 18, when the spring V is restored, if the reverse rotation of the inner ring PO is not even a little, the outer ring PL cannot be rotated to prevent the restoring force of the spring V from acting on the inner ring PO. In the case of FIG. 19, when the spring V is restored and the outer ring PL rotates in the direction of arrow A in the figure, the reverse rotation of the inner ring PO is stopped and the cam body B rotates without any reverse rotation of the inner ring PO. Without sliding, the outer ring PL can be rotated only by sliding along the outer periphery of the inner ring PO. It is possible to prevent the restoring force of the spring V from acting on the inner ring PO.

“The spring V that fixedly supports one mounting shaft on the fixed part W and the other mounting shaft is movably supported on the outer ring PL” forces the outer ring PL to rotate. It becomes more than the power to energize.
For example, if the inner ring PO starts to rotate before the door is fully closed, if the door slowly closes and rotates, the inner ring PO begins to rotate, and at the same time, the outer ring PL rotates reversely, and the cam body B moves to the outer periphery of the inner ring PO. The resistance acting on the door as it moves away from the part is instantly removed.
When the door is closed and rotated rapidly, the restoring force is stored in the spring V until the inner ring PO starts rotating and the outer ring PL rotates and the door decelerates and stops. The door decelerates and stops, and the cam body B moves away from the outer periphery of the inner ring PO, and the resistance acting on the door is removed.

18 (a) and 18 (b) and FIG. 19 (a) and FIG. 19 (b), there is a difference between the rotational motion and the linear motion. The structure of the mechanism is the same, and the rotational motion with an infinite radius is a linear motion, and the number of cam bodies differs between the rotational motion and the linear motion. The same. Each cam body is a one-way check valve that drives and idles, and a check valve is used in a portion that transmits force.

This is a mechanism in which the pressing force is applied perpendicular to the moving direction of the moving body, and is integrated with the moving body due to the wedge effect or friction, and a small rotational force is applied perpendicular to the large pressing force direction to move away from the moving body. Thus, the movement of the contact point between the cam body and the moving body is small in the pressing force direction and large in the direction perpendicular to the pressing force direction.
The operation of the device when the spring is restored is different from the operation of the device when the spring is expanded or contracted. The operation of the device during the expansion and contraction of the spring is an operation to support a large door inertia force, and the operation of the device at the time of restoration is an operation to remove the device that supports the door inertia force, and the cam body B has a large door inertia force. The resistance acting on the door is released by a small rotational force acting in the circumferential direction.

In FIG. 20 as well, a speed reducer provided with a “mechanism that prevents a spring from being pushed back even when pushed in” will be described.
The moving body D and the moving body S move along a predetermined track Zm provided in the fixed portion W, and the movable pulley Bs is mounted on the support shaft Is provided in the moving body S. The moving body SS moves along a predetermined track Zss provided in the fixed portion W, and the rotating body J is rotatably supported around a connection axis C provided in the moving body SS. A link A is rotatably supported around a connecting shaft P provided on the rotating body J.
The tension spring V fixedly supports one mounting shaft on a support shaft Sv provided on the fixed portion W, and movably supports the other mounting shaft on the connecting shaft P. The string N has one mounting shaft fixedly supported on a support shaft Sn provided on the fixed portion W, and moves around the pulley Bn mounted on the support shaft Sv provided on the fixed portion W, and moves the other mounting shaft. It is movably supported on a spindle In provided on the body SS.

FIG. 20A shows a standby state before the moving body D moving in the direction of arrow B in FIG. The link A is urged by the push spring Ua, and the ratchet pawl attached to the tip of the link A presses the rack Ko provided on the fixed portion W, and the tip of the link A slides along the rack Ko. To do. The rack Ko is provided with serrations, and the serrations allow the tip of the link A to move in the direction of arrow A in the figure and prevent it from moving in the direction opposite to arrow A in the figure.
The tension spring V is between the contact Gj provided on the moving body SS and the connection shaft C, and the rotating body J comes into contact with the contact Gj and stops.

In FIG. 20B, the moving body D abuts on the moving body S and moves relatively integrally with the moving body, and the movable pulley Bs presses the string N to expand the pulling spring V, thereby exercising. The state where body D is decelerated is shown.
The moving pulley Bs and the string N are means for converting a slight movement of the moving body D into a large movement of the moving body SS, and by converting a slight rotation into a large rotation speed by a gear mechanism, A slight movement can be a large movement of the moving object SS.
The dynamic inertia force and the force Fd biased in the direction of arrow B in the figure act on the moving body D, and the amount of decrease in the dynamic inertia force acting on the moving body D is stored in the restoring force in the pulling spring V, and the moving body Until D decreases and the speed is lost, the tension spring V is stretched and the restoring force is stored. The amount by which the tension spring V is stretched changes according to the magnitude of the dynamic inertia force of the moving body D, and the greater the dynamic inertia force, the greater the deceleration.

When the speed of the moving body D disappears and stops, the restoring force of the tension spring V is maximized. FIG. 20C shows that the link A is centered on the “contact point b between the tip end of the link A and the rack Ko” while the pulling spring V is restored and the moving body SS is pulled back in the direction of the arrow B in the figure. A state of rotating in the direction of arrow C is shown. Even if the moving body SS is slightly reversed, the backward movement of the movable pulley Bs is further slight.
When the connecting shaft P revolves around the contact b in the direction of the arrow C in the figure, the pulling spring V crosses the connecting shaft C, the direction in which the pulling spring V biases the rotating body J is reversed, and the pulling spring V The resilience of is reduced.
After decelerating, the rotating body J continues to rotate in the direction of arrow D in the figure, and the restoring force of the tension spring V is lost. The resistance that slows down the moving body D is automatically removed. The moving body D starts to move in the direction of arrow B in the figure.

The wheel Bj is mounted on a support shaft Sj provided in the fixed portion W, and when the rotating body J continues to rotate in the direction indicated by the arrow D in the figure, the rotating body J moves along the wheel Bj as shown in FIG. When moved, the moving body SS moves in the direction of arrow A in the figure, the string N is loosened, and the resistance that decelerated the moving body D is further removed.
The wheel Bjj is mounted on a support shaft Sjj provided on the fixed portion W, and when the moving body SS is moved in the direction opposite to the arrow A in the figure and returned to the initial position, as shown in FIG. When the rotating body J rotated in the direction of the middle arrow D is moved along the wheel Bjj as shown in FIG. 20 (a), the tension spring V crosses the connecting shaft C and the rotating body J J hits Gj and comes to rest.

It is desirable that the force for accelerating the moving body does not work while the moving body is decelerated.
The rotating body rotator JJ that is rotatably supported around the support shaft Sj is urged in the direction of arrow E in the figure by the push spring UU. The connecting shaft PP is connected to an urging device (not shown), and the urging device (not shown) urges the moving body D in the direction of arrow B in the figure.

While the wheel Bi is attached to the support shaft In and the rotating body JJ moves along the wheel Bi, the rotating body JJ does not rotate. If the rotating body JJ comes into contact with the wheel Bi when the moving body D comes into contact with the moving body S, the moving body D starts decelerating and at the same time, the urging device (not shown) does not urge the moving body D. . The wheel Bi continues to move in the direction of arrow A in the figure, and when the wheel Bi leaves the rotating body JJ, the rotating body JJ begins to rotate again. At the same time as the deceleration of the moving body D ends, an urging device (not shown) starts to urge the moving body D.

FIG. 21 is a diagram that allows effective work to be performed by the strain energy of the elastic spring while absorbing the kinetic energy of the moving body. After the moving body stops, the spring is restored and the moving body does not move backward. In addition, it starts to advance in the direction of travel.
FIG. 21 (a) is the same as FIG. 17 (b) except that the rack KK is provided in the fixed portion W in parallel with the rack K with the ratchet gear B interposed therebetween, and the teeth of the rack KK face each other in parallel with the teeth of the rack K. The ratchet gear B away from the rack K starts to advance in the traveling direction along the rack KK.
The moving body D is biased by a biasing means Fd (not shown) and moves in the direction of arrow B in the figure along the track Zm provided in the fixed portion W while being relatively integrated with the moving body S.

In FIG. 21A, the rotating body J is rotatably supported around a connection axis C provided on the moving body S. A ratchet gear B is mounted on a wheel support shaft Ib provided at the tip of the rotating body J. In FIG. 21, the rotating body J presses the rack K with a pressing spring U and meshes with the teeth of the rack K. The rack KK is set at a position where the ratchet gear B does not mesh with the teeth of the rack K and the teeth of the rack KK at the same time. The rotating body JJ is rotatably supported around a connection shaft C provided on the moving body S, and a ratchet claw Ra is attached to a wheel supporting shaft Ia provided at the tip of the rotating body JJ.

One attachment shaft of the tension spring V is fixedly supported on a support shaft C provided on the rotating body J, and the other attachment shaft is fixedly supported on a support shaft Sb provided on the ratchet gear B.
As shown in FIG. 21 (a1), while the moving body D moves in the direction indicated by the arrow B in the figure, the ratchet gear B moves along the rack Ko in the direction indicated by the arrow B in the figure. Rotate in the direction. The tension spring V is wound around the winding portion Kb provided on the spur gear B and stretched. The ratchet pawl Ra moves along the ratchet gear B by pressing the ratchet tooth of the ratchet gear B by the push spring Ur. Does not stop.

FIG. 21 (a2) is a state diagram when the moving body D is stopped and the pulling spring V is restored. By the restoring force of the pulling spring V, the ratchet gear B is opposite to the arrow a in the figure, and the ratchet pawl Ra is The ratchet gear B meshes with the ratchet teeth of the ratchet gear B to prevent the ratchet gear B from rotating in the direction opposite to the arrow a in the figure. The rotating body J rotates in the direction of the arrow C in the figure, and the ratchet gear B is separated from the rack K. After the moving body D stops, the pulling spring V is restored, so that it does not return.
The ratchet gear B meshes with the rack KK and moves along the rack KK in the direction of arrow B in the figure. The ratchet pawl Ra remains engaged with the ratchet tooth Rj, but is urged by the push spring Uc to rotate the rotating body JJ in the two directions of the arrow in the figure, and the ratchet gear B rotates in the direction opposite to the arrow i in the figure. .

FIG. 21B shows a rotating body J of FIG. 21A that is rotatably supported around a connection axis C provided on a plate PL attached to the door D. The moving body S is a plate PL. A link AA is rotatably supported around a connection shaft PP provided on the movable body S, and a rack K and a rack KK are provided on the moving body S. A rotating body J and a rotating body JJ are rotatably supported around a connection axis C provided on the plate PL, and a ratchet gear B is mounted on a wheel supporting shaft Ib provided at the tip of the rotating body J. The other parts of the speed reducer in FIG. 21A are attached to the speed reducer in FIG. 21B, and perform the same operation to perform the function of shaking.

As shown in FIG. 21 (b1), the moving body S is mounted with a wheel B that comes in contact with and separates from the sliding surface Kg provided on the door frame W, and before the wheel B contacts the sliding surface Kg, S is urged by the push spring Us in the direction rotating in the direction opposite to the arrow D in the figure, and the rotation in the direction opposite to the arrow D in the figure is blocked by Gs and stands still.
When the door D rotates about the pivot O in the direction indicated by the arrow B and the wheel B moves along the sliding surface Kg, the moving body S rotates about the connecting shaft PP in the direction indicated by the arrow D in the figure. . The magnitude of the force of the biasing means Fd (not shown) that biases the door D so as to rotate in the direction indicated by the arrow B in the drawing is sufficiently larger than the push spring Us.

The rotating body J is indirectly biased by the push spring Uc in the direction in which the ratchet gear B moves away from the rack K, and while the rotation of the moving body S is blocked by Gs, the starting end KKs of the rack KK The ratchet gear B meshes with the rack K and waits.
When the wheel B comes into contact with the sliding surface Kg, the moving body S hits and rotates away from Gs, and the ratchet gear B moves away from the starting end KKs of the rack KK, but does not mesh with the rack K when the rotational speed of the door is small. Leave rack K. When the rotational speed of the door is high, the ratchet gear B meshes with the rack K and rotates in the direction indicated by the arrow E in the figure while moving along the rack K in the direction indicated by the arrow.

One attachment shaft of the tension spring V is fixedly supported by the connection shaft C, and the other attachment shaft is movably supported by a support shaft Sb provided on the ratchet gear B. When the ratchet gear B rotates in the direction of arrow E in the figure, the pulling spring V is wound around the winding portion Kb provided on the ratchet gear B and is stretched.
When the door is decelerated by the extension of the tension spring V and the door stops, the tension spring V is restored, and the ratchet gear B is rotated in the direction opposite to the arrow H in the figure. The ratchet pawl Ra meshes with the ratchet teeth of the ratchet gear B, thereby preventing the ratchet gear B from rotating in the direction opposite to the arrow a in the figure. The rotating body J rotates about the connecting shaft C in the direction of the arrow C in the figure, and the ratchet gear B is separated from the rack K. After the door D is stopped, the tension spring V is restored, so that it does not start to rotate in the opening direction.

The rotating body J is indirectly moved by the push spring Uc, and the ratchet gear B is separated from the rack K, meshes with the rack KK and rotates in the direction opposite to the arrow H in the figure, and rotates the moving body S in the direction of the arrow D in the figure. Let As shown in FIG. 21 (b2), the wheel B moves away from the sliding surface Kg, the resistance that has been applied to the door until then is released, and the door is fully closed.

In a device in which the spring is restored after the door is stopped and the resistance that has been applied to the door is released, the spring prevents or uses the restoration to cut the restoring force of the spring. Thus, the reverse rotation prevention means and the one-way clutch restricting operation in one direction are used. However, even if the ratchet mechanism or the one-way clutch is adopted, the restoring force of the spring is cut off. Before, the door rotates in a slightly opening direction.
FIG. 22 illustrates some simple structures where the door rotates slightly in the opening direction when the restoring force of the spring is cut. 22 (a1), FIG. 22 (b1), FIG. 22 (c1), and FIG. 22 (d1) are state diagrams immediately before cutting the restoring force of the spring in each structure, and FIG. 22 (b2), 22 (c2), and 22 (d2) are state diagrams immediately after.

The moving body D is urged by an urging means Fd (not shown) and moves in the direction of arrow B in the figure along a track Zm provided on the fixed portion W. In addition, a check device (not shown) that prevents movement in the direction opposite to the arrow B in the figure is provided. The moving body S contacts the moving body D at the contact b through the rotating body J, and expands and contracts the deceleration spring. The rotating body J is pivotally supported around the connecting shaft C, and the connecting shaft C is provided on the moving body D in FIGS. 22 (a), 22 (b), and 22 (c). In d), the moving body S is provided.

The deceleration spring is a push spring U in FIGS. 22 (a), 22 (b), and 22 (d), and a tension spring V in FIG. 22 (d). One mounting shaft of the deceleration spring is fixedly supported by the fixing portion W, and the other mounting shaft is supported by the moving body S.
The moving body D decelerates while expanding and contracting the deceleration spring, and at the same time the moving body D stops, in FIG. 22 (a), FIG. 22 (b), FIG. Rotate S. In FIG. 22D, the restoration of the deceleration spring is prevented and the moving body S is not rotated. As soon as the moving body D stops, the deceleration spring does not act on the moving body D, and the moving body D can move in the direction of arrow B in the figure without receiving the resistance of the deceleration spring.

To prevent the moving body D from moving in the direction opposite to the arrow B in the figure after the deceleration spring is restored, the movement of the moving body S must be different from when the deceleration spring expands and contracts. Do not reciprocate in the same direction, only when the direction is reversed, when expanding and contracting. In order not to reciprocate the same movement, a restraining means for restraining the movement of the moving body S when expanding and contracting and a check device for preventing the movement direction of the moving body S from reversing when restoring are required.

In FIG. 22A, the connecting shaft CC is provided on the moving body S, and the cam body B whose outer periphery shown in FIG. The cam body B moves along the sliding surface Kw provided in the fixed portion W so that the push spring U is restored and the connection shaft CC does not return. The two push springs U are contracted to the same length as much as possible when the deceleration spring is expanded and contracted so that the movable body S moves as little as possible. S rotates around the connecting axis CC while moving the moving body backward through the rotating body J.

22B, the moving body SS moves in the direction of arrow B in the figure along the track Zs provided in the fixed portion W. In FIG. 22C, the moving body SS is the track Zm provided in the fixed portion W. Move in the direction of arrow B in the figure. 22 (b) and 22 (c), the moving body S is rotatably supported around the connection axis CC provided on the moving body SS, and the moving body S is connected to the connection axis by the dynamic inertia force of the moving body D. Gs is provided for the mobile object SS so as not to rotate around the CC.

In FIG. 22B, the wedge B is urged by the push spring Ub and moves along the sliding surface Kw provided on the fixed portion W, while supporting the end SSb of the moving body SS, and the push spring U. Is restored so that the connecting axis CC does not return. In FIG. 22 (c), the ratchet pawl Ra is attached to the connecting shaft CC, and the ratchet pawl Ra meshes with the saw tooth provided on the rack Ko so that the pulling spring V is restored so that the connecting shaft CC does not return.
22 (b) and 22 (c), when the moving body D stops and the dynamic inertia force disappears, the deceleration spring is restored, and the moving body S moves the moving body back through the rotating body J. , Rotate around the connection axis CC.

22 (a), 22 (b), and 22 (c), the sliding surface Ks is provided on the moving body S and contacts the tip of the rotating body J at the contact b. The line of action of the force Fb that the sliding surface Ks presses the contact b passes between the connecting shaft C and the contact Gd when the reduction spring is expanded and contracted, and the contact Gd prevents the rotating body J from rotating. At the time of restoration of the deceleration spring, the moving body S rotates, so that the contact b moves along the sliding surface Ks, the action line of the pressing force Fb crosses the connection axis C, and the rotating body J hits away from Gd. Rotate to. The moving body D is free to move in the direction of arrow B in the figure.

In FIG. 22 (d), the moving body S is rotatably supported around a fixed support shaft Sw provided on the fixed portion W, and the moving body D moves in the direction indicated by the arrow B in the figure. Rotate in the direction of the middle arrow a to retract the push spring U. A sliding surface Kd is provided on the moving body D, and contacts the tip of the rotating body J at the contact b. While the moving body D is moving, the sliding surface Kd presses the contact b, and a frictional force acts between the sliding surface Kd and the tip of the rotating body J.

The pressing spring Uj presses the side surface of the rotating body J and urges the rotating body J to rotate about the connecting shaft C. However, as shown in FIG. Does not move the contact b. As shown in FIG. 22 (d2), when the rotation of the moving body S is stopped and the dynamic inertia force of the moving body D becomes weak and the frictional force does not act strongly, the contact b moves and the rotating body J Rotates. The moving body D is free to move in the direction of arrow B in the figure.
As the rotating body J, which has been self-supporting in this way, buckles, the moving body D is less retracted. Although the moving body D is released from the resistance of the deceleration spring, it can also be expected that the restoring force of the deceleration spring will perform work other than the work that releases the resistance acting on the moving body D. For example, it can also be expected to do work that switches on starting a further reduction gear after deceleration.

FIG. 23 is an explanatory diagram of a mechanism for releasing the spur gear B meshed with the rack Ko.
The moving body D moves along a track Zm provided in the fixed portion W by an urging means Fd (not shown). A rotating body J is rotatably supported around a connection axis C provided on the moving body D, and a spur gear B is mounted on a wheel supporting shaft Ib provided at the tip of the rotating body J.
The rotating body J is urged by a push spring U, and the spur gear B is urged away from the rack Ko. One attachment shaft of the tension spring V is fixedly supported on a support shaft Sj provided on the rotating body J, and the other attachment shaft is movably supported on a support shaft Sb provided on the spur gear B.

When the spur gear B is moved along the rack Ko in the direction indicated by the arrow B by the urging means Fd (not shown) and rotates in the direction indicated by the arrow A in the figure, the pulling spring V is wound around the spur gear B. Wound around Kb and stretched. Due to the restoring force of the tension spring V, the spur gear B rotates in the direction opposite to the arrow A in the figure and moves along the rack Ko in the direction opposite to the arrow B in the figure.
At the contact point b between the spur gear B and the rack Ko, a frictional force is generated by the circumferential pressing force of the spur gear B. FIG. 23 (a1) shows that when the axial center line Zj of the rotating body J and the rack Ko are parallel, the frictional force exceeds the “separation force Fv that attempts to separate the spur gear B from the rack Ko by the push spring U”. Thus, the spur gear B does not leave the rack Ko.

The crossing angle Θ is an angle Θ where the axis core line Zj of the rotating body J and the rack Ko intersect, and is an area divided by the rack Ko and including the spur gear B and is divided by the axis core line Zj of the rotating body J. The angle Θ of the region that is rearward with respect to the traveling direction of the spur gear B in the region.
FIG. 23 (a2) shows the case where the axial center line Zj of the rotating body J and the rack Ko are not parallel and the crossing angle Θ is an acute angle, and FIG. 23 (a3) shows the case where the crossing angle Θ is a right angle. FIG. 23 (a4) shows a case where the crossing angle Θ is an obtuse angle.

As shown in FIG. 23 (a2), a biasing means Fd (not shown) that biases the moving body D is caused by a force Fb that returns the spur gear B along the rack Ko in the direction opposite to the arrow B in the figure by the pressing spring U. When it is larger, the spur gear B moves along the rack Ko in the direction indicated by the arrow B in the figure, and rotates the rotating body J in the direction indicated by the arrow C in the figure. When the biasing means Fd is larger than the returning force Fb, the spur gear bites into the back of the rack Ko, and the spur gear shifts to a state in which it is more difficult to separate from the rack Ko. When the spur gear continues to advance, the force that meshes with the rack Ko increases, and the state shifts to a state in which it is more difficult to leave the rack Ko. On the contrary, when the spur gear moves backward, the force that meshes with the rack Ko decreases, and the state shifts to a state where it is more easily separated from the rack D.

When the biasing means Fd is smaller than the returning force Fb, the spur gear B moves along the rack Ko in the opposite direction to the arrow B in the figure, and rotates the rotating body J in the opposite direction to the arrow C in the figure. The rotating body J rotates in a direction in which the spur gear B is separated from the rack Ko, and the spur gear is shifted to a state where it is more easily separated from the rack Ko.
When the spur gear B starts to reversely rotate, the spur gear B slightly moves along the rack Ko in the direction opposite to the arrow B in the figure. Unlike the ratchet gear, the spur gear B leaves the rack Ko with almost no return in the reverse direction when leaving the rack Ko.

When the biasing means Fd is a dynamic inertia force acting on the moving body D, the moving body D reduces the dynamic inertia force while reducing the movement speed while moving in the direction of arrow B in the figure, and restores the tension spring V. Increase power. When the dynamic inertia force disappears, the restoring force of the push spring U reaches the maximum with the moving body D stopped. When the moving body D stops, the spur gear B starts to reversely rotate, and the spur gear leaves the rack Ko.

Whether or not the spur gear B is separated from the rack Ko depends on the force relationship between the biasing means Fd and the return force Fb. Leave the rack Ko.
However, as shown in FIG. 23 (a4), when the rotating body J is rotated in the direction opposite to the arrow C in the figure when the crossing angle Θ is an obtuse angle, the rotating body J does not leave the spur gear B from the rack Ko. And the spur gear does not leave the rack Ko. As shown in FIG. 23 (a3), the contact Gj is provided so that the crossing angle Θ does not become larger than a right angle.

As shown in FIG. 23 (a1), when the track Zm and the rack Ko are parallel, the crossing angle Θ varies depending on the distance between the track Zm and the rack Ko as shown in FIG. 23 (b1). When the track Zm and the rack Ko are not parallel, the crossing angle Θ varies depending on the curvature of the track Zm as shown in FIG. 23 (b2).
23 (b1) and 23 (b2) show that the moving body U moves from the position shown in FIG. 23 (b1) to the position shown in FIG. 23 (b2) along the trajectory Zm in the direction of arrow B in the figure. The crossing angle Θ increases while the gear B moves along the curved rack Ko.

Whether or not the spur gear B is difficult to be separated from the rack K is determined not only by the force relationship between the biasing means Fd and the return force Fb but also by the magnitude of the crossing angle Θ, as shown in FIG. 23 (b2). In addition, the closer the rack Ko is to the orbit Zm, the greater the resistance of the moving body D to progress. Further, the spur gear B will not be separated from the rack K unless the moving body D is retreated greatly. The spur gear B will not leave the rack D unless the force that the moving body D continues to move forward disappears and begins to move backward.
23 (b1) and 23 (b2), as the moving body D progresses, the resistance acting on the progress of the moving body D gradually increases as the rack Ko approaches the trajectory Zm at a right angle. The spur gear B is prevented from moving away from the rack K before the force to continue moving forward is lost.

FIG. 24 is obtained by incorporating the speed reducer introduced in FIG. 23 into the door of Patent Document 1 described in FIG. 2 so that the door is quietly fully closed.
The door D rotates around the pivot axis O in the direction of arrow B in the figure, and the rotating body J rotates around the connection axis C provided on the door D in the direction of arrow A in the figure. The link A connects a connecting shaft P provided at the tip of the rotating body J and a fixed support shaft Sw provided on the door frame W.
FIG. 24A is a state diagram when the speed reducer starts at the end of the range (A), FIG. 24B is a state diagram during deceleration, and FIG. 24C is a state diagram when the door is fully closed. Indicates.

The range of (A) and (I) is distinguished from the predetermined opening degree of the door immediately before full closure, and within the range (A), the rotation of the door is large and the rotating body J rotates small, In the range of (ii), the rotation of the rotating body J is greatly rotated with little door rotation. In the range of (ii), the rotation of the rotating body J is completed at a high speed in an instant, so the door is fully closed without being decelerated. The speed reducer shown in FIG. 24 slowly rotates the rotating body J in the range of (Yes) to slowly fully close the door.
The speed reducer of FIG. 24 operates with a spring prepared separately from the spring that biases the door, starts to start at a predetermined opening degree of the door, and when fully closed, the resistance that has acted on the door until then is automatically Has been released.

A link AA is rotatably supported around a connecting shaft PP provided on the rotating body J, and a rack Ko is provided on the link AA. A rotating body JJ is rotatably supported around a connection shaft CC provided on the rotating body J, and a spur gear B is mounted on a wheel supporting shaft Ib provided at the tip of the rotating body JJ.
One attachment shaft of the tension spring V is fixedly supported on a support shaft Sj provided on the rotating body J, and the other attachment shaft is movably supported on a support shaft Sb provided on the spur gear B. When the spur gear B moves along the rack Ko in the direction indicated by the arrow D and rotates in the direction indicated by the arrow E in the figure, the tension spring V is wound around the winding portion Kb provided on the spur gear B and stretched.

The rotating body Jv is pivotally supported at the intermediate portion so as to be rotatable around the connection axis CC.
The rotating body JJ is energized by a toggle spring VV, one mounting shaft of the toggle spring VV is fixedly supported on a wheel support shaft Ib provided on the rotating body JJ, and the other mounting shaft is fixed on a support shaft Sb provided on the rotating body Jv. Supported. The rotating body Jv is pivotally supported at the intermediate portion so as to be rotatable around the connection axis CC, and swings between the hit G1 and the hit G2. The rotating body Jv is provided with a support shaft Sb at one end with the connecting shaft CC in the middle, and the end Ja opposite to this has a portion that contacts and separates from the “contact portion Ga provided on the link A”. Prepare.

As shown in FIG. 24 (a), until the predetermined opening degree of the door immediately before full closing, the rotating body Jv comes into contact with G2 and is stationary, and the spur gear B presses the rack Ko. As shown in FIG. 24B, the intersection angle Θaj between the rotating body J and the link A starts to decrease sharply at a predetermined opening degree of the door immediately before full closing, and the rotating body J starts to move greatly. Then, the abutting portion Ga pushes the end portion Ja on the opposite side to rotate the rotating body Jv so that it comes into contact with G1 and comes to rest. The toggle spring VV crosses the connecting shaft CC, and the direction in which the rotating body JJ is urged is switched to the direction in which the spur gear B is separated from the rack Ko.

The wheel BB is attached to the link AA, and the link AA moves along the sliding surface Kw provided on the door frame W at a predetermined opening degree of the door immediately before full closing. Rotate. When the direction in which the toggle spring VV urges the rotating body JJ reverses and the door D rotates slowly, the spur gear B moves away from the rack Ko. When the door D rotates at a high speed, the spur gear B meshes with the rack Ko before the spur gear B moves away from the rack Ko, and rotates in the direction indicated by the arrow E in the figure.
The pulling spring V is wound around the winding portion Kb and stretched, and the door is decelerated. However, when the door D is decelerated and rotates at a low speed, the spur gear B is separated from the rack Ko.

The speed reducer in FIG. 24 uses door inertia force for resistance, and the resistance depends on the magnitude of the door inertia force. When the door inertia force is large immediately before full closing and the door rotates at high speed, the resistance acting on the door is large, and when the door inertia force is small and the door rotates at low speed, the reduction gear does not function.
When the spur gear B comes into contact with the terminal end Koe of the rack Ko, the link AA cannot rotate and the door D cannot rotate. While the door is completely closed, the rotary body JJ is rotated in the direction of the arrow in the figure by the toggle spring VV, and the spur gear B fits into the recess Kob as shown in FIG. 24 (c). Then, the door starts to rotate again, rotates slightly, and is fully closed.

Decreasing the door rotation speed to zero in the slight rotation range of the door from immediately before full closure to full closure gives the door an impact close to a collision, and allows the door rotation range to decelerate the door. It should only be enlarged and sudden deceleration should be avoided. In the embodiment of FIG. 24, the connecting shaft CC of the rotating shaft of the rotating body JJ and the connecting shaft PP of the rotating shaft of the link AA are provided in the movable rotating body J to mitigate rapid deceleration. Further, when the connecting shaft CC and the connecting shaft PP are directly provided on the door D so that the spur gear B moves along the rack Ko, the reduction gear of FIG. 24 rapidly decelerates the door.
When the position where the spur gear B first contacts the sliding surface Kw is located farther from the pivot axis O than the connection axis C, and the force that rotates the rotating body J in the direction opposite to the arrow A in the figure is applied, The movable rotating body J is stationary and is the same as the case where the connecting shaft CC and the connecting shaft PP are directly provided on the door D. The degree to which the door is rapidly decelerated can be adjusted by the position where the spur gear B first contacts the sliding surface Kw.

24, when the connecting shaft CC and the connecting shaft PP are directly provided on the door D, the rotating shaft C of the contact rotating body J and the rotating shaft PP of the moving body S are provided on the plate PL provided on the door D in FIG. Even if the speed reducer is attached in any way, the door closer is also indirectly decelerated if the door is directly decelerated if the door and the door closer are interlocked. 24, when the connecting shaft CC and the connecting shaft PP are directly provided on the door D, the rotation of the rotating body J is also decelerated.

From the middle of the rotation of the door in the closing direction, the rotation speed of the door accelerates and accelerates. Therefore, as the door starts to rotate in the closing direction, the door rotates greatly in a shorter time. In contrast, when the door starts to rotate in the closing direction, the rotational speed of the door gradually increases from zero, and the door rotates slightly over a relatively long time. When the door starts to rotate in the closing direction, a force exceeding the maximum static friction force acting on the door is required, but a force exceeding the kinetic friction force smaller than the maximum static friction force is sufficient from the middle of the rotation. As the force exceeding the maximum static friction force continues to act on the door, the acceleration of the door is further increased.
FIG. 25 intermittently applies a force exceeding the maximum static frictional force to the door in order to reduce the acceleration of the door that is closed from the fully open position. The spring that biases the door repeats restoration and restoration stop, and the door also repeats rotation and rotation stop.

The hinge shown in FIG. 25 is composed of a sliding bearing Q, an upper spline bearing QQ1, a lower spline bearing QQ2, and a pin OP. One of the sliding bearing Q and the upper and lower two spline bearings QQ is attached to the door frame W. , The other attaches to door D.
As shown in FIG. 25 (b), the upper spline bearing QQ1 and the lower spline bearing QQ2 are arranged with the sliding bearing Q in the middle, and the pin OP is connected to the sliding bearing Q, the upper spline bearing QQ1, and the lower side. The spline bearing QQ2, the torsion spring Vd, and the thrust bearing Qs are inserted, and the pin OP is movable in the axial direction.

The torsion spring Vd biases the door D, one mounting shaft is fixedly supported by the door frame W, and the other mounting shaft is movably supported by the door D via the sliding bearing Q. The pulling spring V biases the pin OP in a pulling-down direction, one mounting shaft is fixedly supported by the door frame W, and the other mounting shaft is movably supported by a support shaft Sv provided at the lower end of the pin OP.
The string N connects the door D and the pin OP and converts the rotation of the door D into the vertical movement of the pin OP. One side of the string N is attached to a support shaft Sd provided on the door D, On the way, it moves along the water smooth pulley Bk1 and the vertical pulley Bk2, and the other end of the string N is attached to a support shaft Sn provided at the upper end of the pin OP. FIG. 25A is a plan view and FIG. 25B is an elevation view.

The pin OP is supported by the sliding bearing Q and the two upper and lower spline bearings QQ so as to be movable along the pivot axis O without rotation. Near the both ends of the pin OP are the processing parts OP1 and OP2, and the part that moves along the spline bearing QQ is splined. An intermediate portion of the pin OP is a cylindrical portion OP3 that is not subjected to spline processing. A sliding bearing Q is rotatably supported around the cylindrical portion OP3. The sliding bearing Q allows rotation of the pin OP and movement in the rotation axis direction, and two upper and lower spline bearings QQ are arranged in the rotation axis direction of the pin OP. Allow movement but prevent rotation of pin OP.

As shown in FIG. 25 (c), the boss B is a cylinder that is planted in the sliding bearing Q and protrudes from the inner surface of the sliding bearing Q. The groove M is formed in the cylindrical portion OP3, the width of the groove M is equal to or greater than the diameter d of the boss B, and the depth is equal to or greater than the height h at which the boss B protrudes from the inner surface of the sliding bearing Q.
As shown in FIG. 25 (c), the boss B moves along the outer periphery of the sliding bearing Q and makes a circular motion on the same plane Wo. FIG. 25C is a sectional view of the boss B cut horizontally, and FIG. 25C is a sectional view of the boss B cut along a vertical plane.

The groove M does not rotate around the pivot axis O and moves up and down along the pivot axis O. The boss B moves along the groove M between the start end Ms and the end Me of the groove M. When the boss B is at the position of the terminal end Me of the groove M, the door D is lowered down the pin OP through the string N and the door D is fully closed. When the boss B is at the position of the starting end Ms of the groove M, the door D is fully opened and the pin OP is pulled up to the highest.

FIG. 25 (e) is a development view of the groove M formed on the surface of the cylindrical portion OP3. The height Ho is the head of the pin OP, and the length Lo is the length of the outer periphery of the cylindrical portion OP3 corresponding to the rotation angle of the door D. That's it.
The spiral groove M is partially expressed as a straight line M2 in a developed view, and the lead angle Θo is an intersection angle between the plane Wo and the center line of the groove M. The lead angle Θo varies depending on the rotation angle of the door D, is small near the start end portion Ms, and approaches 90 degrees near the end portion Me. When the lead angle Θo is small, the resistance to the circular motion of the boss B is small, and when the lead angle Θo is large, the resistance is large. When the lead angle Θo is 90 degrees, the circular motion of the boss B stops and the rotation of the door stops.

Assuming that the moving speed of the pin OP in the rotation axis direction is constant, the smaller the lead angle Θo, the faster the door D rotates. Immediately before the door D whose lead angle Θo is 90 degrees is fully closed, the door D is temporarily stopped.
When the lead angle Θo is zero, only the torsion spring Vd is restored, and when the lead angle Θo is 90 degrees, only the tension spring V is restored, and the torsion spring when the lead angle Θo is between zero and 90 degrees Vd and tension spring V are restored simultaneously. Either the torsion spring Vd or the tension spring V is always restored, and it does not remain stopped even if the door stops.

In the development view of the groove M, in the stepped M1 portion, the torsion spring Vd and the pulling spring V alternately repeat restoration and restoration stop, and the door repeats rotation and stop alternately. Even if the return spring Vd and the tension spring V alternately repeat restoration and restoration stop, static inertia and dynamic inertia work alternately on the door D, and the door D alternately repeats acceleration and deceleration, apparently, It appears to rotate at a constant speed.

On the good side of the groove M, the deceleration sliding surface KK and the acceleration sliding surface K face each other, the front side in the direction of travel of the boss B is the deceleration sliding surface KK, and the rear side is the acceleration sliding surface K. It is. When the boss B moves along the acceleration sliding surface K, the door accelerates, and when the boss B moves along the deceleration sliding surface KK, the door decelerates. When the movement of the boss B is delayed, the acceleration sliding surface K pushes the boss B from the rear, and when the movement of the boss B is accelerated, the front deceleration speed sliding surface KK hinders the progress of the boss B.
However, since the spring is restored in an instant, the torsion spring Vd continues to press the boss B against the deceleration speed sliding surface K without loosening. Boss B does not leave the deceleration speed sliding surface KK.

The deceleration speed sliding surface KK is about to move backward, and the position where the boss B is prevented from moving back. Further, the rotation preventing means for the door D is retracted. The boss B is a moving body, and the decelerating speed sliding surface KK is a moving body that moves relative to the moving body on the same plane Wo. The moving body moving at high speed and the moving body moving at low speed influence each other, the moving body decelerates and the moving body accelerates.
As the door D rotates at a higher speed, the door inertia force increases, the force with which the boss B presses the deceleration speed sliding surface KK increases, and the frictional force resisting the movement of the boss B increases. The door is greatly decelerated as the door D rotates at high speed.

This effect increases as the lead angle Θo increases, and increases as the pin OP moves up and down greatly. The more the pin OP moves up and down with respect to the rotation of the door, the more resistance the boss B moves. The smaller the vertical movement of the pin OP with respect to the rotation of the door, the more the boss B is moved by the door, and the door does not decelerate.
If the force of the tension spring V is increased, the vertical movement speed of the pin OP increases, and the boss B cannot be decelerated unless the lead angle Θo is increased. If the force of the tension spring V is weakened, the vertical movement speed of the pin OP is reduced. However, if the lead angle Θo is not reduced, the boss B may remain stopped.

However, when the boss B remains stopped, the door inertia force becomes zero when the door D stops, the boss B does not press the deceleration sliding surface KK, and resistance to the movement of the boss B is lost. Disappear. Boss B starts moving even if it stops. Door D does not remain stationary.
Even considering the effect that the inertia of the door becomes zero when the door D stops, it is difficult to adjust the lift of the pin OP and the strength of the tension spring V, and a simple resistance to slow down the recovery of the tension spring V should be added. Is desirable. For example, the speed reduction means Rj1 shown in FIG. 1 can be solved by inserting it in the middle of the string N even if it is not inside the hinge.

When the latch of the door D comes into contact with the door frame W and begins to dent, the force to rotate the door D is the maximum, and the force required to open the fully closed door is the door D while the latch is depressed. Must be more than the force to rotate. To minimize the force required to open a fully closed door, the door stops once after the latch begins to dent, and the latch dents while the door is moving. If you release your hand while the latch is in contact with the door frame W, the door will remain stopped, but when the latch is in contact with the door frame W, the door D is rarely stopped. It is more convenient for many uses to reduce the total closing force by using.

Immediately before the door is fully closed, the groove M3 is parallel to the pivot axis O and the boss B stops. However, the door D pulls down the pin OP through the string N, and the boss B indicates that “the lead angle Θo is slightly less than 90 degrees. By moving along the small portion M4 ”and revolving gradually, the door D does not accelerate rapidly in the range of (Yes), and the force Fd acting on the door suddenly increases. Close it quietly.
In addition to the torsion spring Vd that urges the door in this way, by providing the pull spring V that pulls down the pin OP, the door D and the door that moves backward while restraining the door do not stop at the same time. The link device consisting of the door closer continues to move. The door closes without stopping.

FIG. 26 is an explanatory diagram of a loading platform TA on which a load to be attached to the ceiling is placed, and is an explanatory diagram of the loading platform TA that moves up and down. A balancing device that is stationary at an arbitrary height of the loading platform TA regardless of the weight of the loading. And an explanatory diagram of the speed reducer that causes the loading platform TA to repeatedly stop and rise and fall.
The loading platform TA is connected by a fixed portion W provided on the ceiling and two links Ab and Ak having the same length. The loading platform TA and the fixed portion are links of the same length, and the link Ab, the link Ak, and the loading platform TA form a link device of a four-bar rotation mechanism, and link shafts Swb, Swj, Cb, Cj are formed. The figure is a parallelogram. The loading platform TA is always kept level.

FIG. 26 (a) is a diagram for explaining the operation of the balance device and the speed reducer. The reference numerals 0 to 5 indicate that the height of the loading platform TA is divided into five stages in ascending order. For example, the link Ab3 is TA3. It corresponds to.
FIG. 26B is a state diagram when the loading platform TA is lowered, and FIG. 26C is a state diagram when the loading platform TA is raised. In the figure, the arrow A direction is the rotation direction when each link descends, and the arrow B direction in the figure is the rotation direction when each link descends.
The groove MT is provided in the loading platform TA, and the wheel support shaft Ib moves along the groove MT. At the same time, the wheel B mounted on the wheel support shaft Ib moves in the groove Mw in which the fixing portion W is provided. The groove Mw is a path of the zigzag wheel B and includes a sliding surface K and a sliding surface KK. The sliding surface K and the sliding surface KK face each other and are stepped sliding surfaces each having a horizontal portion and a vertical portion.

As shown in FIG. 26 (b), when the loading platform TA descends, the wheel support shaft Ib is urged in the direction of arrow A in the figure by an urging means (not shown). When the wheel B moves along the horizontal portion of the sliding surface KK, the loading platform is stopped from descending, and the wheel B is moved in the direction of arrow A in the figure by the urging means (not shown) to move from the horizontal portion of the sliding surface KK. When leaving and abutting against the vertical portion of the sliding surface KK, the loading platform TA descends due to gravity.
In this way, the wheel B moves from top to bottom along the stepped sliding surface KK, and at the same time, the wheel support shaft Ib moves in the direction of the arrow a in the figure while alternately stopping and moving, and the loading platform Ta Keeps descending, repeating stop and descend. When the wheel B is on the sliding surface KK0, the loading platform TA does not descend any further.

As shown in FIG. 26 (c), when the loading platform TA rises, the wheel support shaft Ib is urged in the direction indicated by the arrow B in the drawing by urging means (not shown). When the wheel B moves along the horizontal portion of the sliding surface K, the lift of the loading platform is stopped, and the wheel B moves in the direction indicated by the arrow B in the figure to move away from the horizontal portion of the sliding surface K. When it comes into contact with the vertical portion, the loading platform TA is raised by the urging means V provided separately from the urging means (not shown) for urging the wheel support shaft Ib.
In this way, the wheel B moves from the bottom to the top along the stepped sliding surface K, and at the same time, the wheel support shaft Ib moves in the direction of arrow B in the figure along the groove MT while alternately repeating the stop and the movement. Then, the loading platform Ta continues to rise while repeatedly stopping and raising. When the wheel B is on the sliding surface K5, the loading platform TA does not rise any further. Moreover, it does not descend any further.

Similar to the embodiment of FIG. 13, the large door inertia force acting on the wheel support shaft Ib is the groove MT and the sliding surface that are perpendicular to the direction of the door inertia force when the loading platform TA is lowered or raised. K or sliding surface KK supports the door. Moreover, the wheel support shaft Ib can move along the groove MT.
When the door D shown in FIG. 13 is replaced with a lid D that rotates about a horizontal rotation axis O, FIG. 13 is an operation explanatory diagram of the process in which the lid D descends.

When the lid D in FIG. 13 rotates around the horizontal rotation axis O, the center of gravity of the lid also rotates around the horizontal rotation axis O, and the rotational moment due to gravity around the rotation axis O changes with the rotation of the lid. , Minimum when lid D stands up, maximum when lying down. In FIG. 13, the distance between the wheel B and the rotary shaft O is the minimum when the lid D is erected and the maximum when it is lying down.
Also in FIG. 26, the rotational moment due to the weight of the loading platform TA acting around the support shaft Swj works in the direction of arrow A in the figure and changes with the rotation of the link Aj. The rotational moment due to weight is maximum when the loading platform TA is fully raised, and is minimal when the loading platform TA is fully lowered. In FIG. 26, the distance Lv between the axial center line Zv of the tension spring V and the support shaft Swj is maximum when the loading platform TA is fully raised and is minimum when the loading platform TA is fully lowered.

The biasing means V provided separately from the biasing means (not shown) for biasing the wheel support shaft Ib is a pulling spring V that rotates the link Aj about the support shaft Swj in the direction indicated by the arrow B in the figure. While acting on the loading platform Ta alternately with the urging means that does not, the suspension and expansion are repeated when the loading platform TA is lowered, and the stopping and restoring are repeated when the loading platform TA is raised.
One attachment shaft of the tension spring V is movably supported by the end portion Ne of the string N, and the other attachment shaft is fixedly supported by a support shaft Sv provided at the tip of the link Av. The link AV is rotatably supported around the connecting shaft Swj, and swings between a contact G0 and a contact G5 provided in the fixed portion W.

The starting end Ns of the string N is fixedly supported by a support shaft Sj provided on the sliding surface Kj provided on the link Aj, and the terminal end Ne of the string N is connected to one attachment shaft of the tension spring V.
Between the starting end Ns of the cord N and the contact b, it adheres closely along the sliding surface Kj and forms a vortex, and from the contact b of the cord N to the end Ne, it is linear and slides. Away from face Kj.
The shape of the outer edge of the sliding surface Kj is the rotational moment due to the force of the pulling spring V acting around the support shaft Swj, and the magnitude is the direction of the arrow B in the figure. It is the product of the distance Lv between the line of action of the V force and the support shaft Swj, and is designed to balance the rotational moment due to the weight of the loading platform TA acting in the direction of arrow A in the figure around the support shaft Swj. .

Even if the loading platform TA is designed to be stationary at an arbitrary position in this way, depending on the load loaded on the loading platform TA, the rotational moment due to the force of the pulling spring V may be insufficient or excessive, but the link Av may be moved to the left and right. It can be adjusted by moving and moving the mounting shaft Sv on the fixed support side of the tension spring V. When the rotational moment is insufficient, the loading platform Tb is lowered, and when it is excessive, the loading platform Tb is raised. The link Av is rotated in the direction of arrow A in the figure to lower the loading platform Tb, and the rotation in the direction of arrow B in the drawing is raised to raise the loading platform Tb.

FIG. 26A shows an example of the shape of the outer edge portion of the sliding surface Kj. Although the loading platform Tb rises due to the restoring force of the tension spring V, the tension spring V becomes shorter and the force decreases as the loading platform Tb rises. When the loading platform TA is fully raised, the strength of the pulling spring V is minimized, and the moment in the direction of arrow A in the figure due to gravity is maximized. When it is fully lowered, the tension spring V strength is maximized and the moment due to gravity is minimized. As the loading platform TA rises, the rotational moment must increase, but the tension spring V strength decreases. Even if the pulling spring V length is extremely large and the loading platform TA rises and the pulling spring V strength hardly decreases like the mainspring spring, the distance Lv must increase as the loading platform TA rises.

If the outer edge of the sliding surface Kj is circular, the distance Lv is constant, and the extension of the tension spring V is proportional to the rotation angle of the link Aj. As the loading platform TA rises, the force of the pulling spring V becomes insufficient, so a circle cannot be adopted.
The shape of the outer edge portion of the sliding surface Kj should not be a vortex line in which the distance from the support shaft Swj to the outer edge portion of the sliding surface Kj simply increases, but a vortex line in which the increase rate of the distance is large.
If the shape of the outer edge portion of the sliding surface Kj is the shape of the sliding surface K described in FIG. 9, the distance from the support shaft Swj to the perpendicular standing on the sliding surface Kj is constant and does not change. . In order to increase the distance to the perpendicular, the virtual circle Rsw shown in FIG. 9 must be a vortex.

The distance to the perpendicular line must be large near the position where the loading platform TA is fully raised, and small near the position where the loading platform TA is fully lowered. Therefore, the change in the distance Lv accompanying the rotation of the link Aj also increases near the position where the loading platform TA has fully raised, and decreases near the position where the loading platform TA has fully lowered. However, the rate of increase of the moment in the direction of arrow A in the figure due to gravity is not constant, it is small near the position where the loading platform TA has been fully raised, and is large near the position where it has fully lowered. The distance to the perpendicular must increase at an accelerated rate as the platform TA descends.

When the virtual circle Rsw shown in FIG. 9 is a vortex, the change in the distance Ls from the support shaft Swj to the vortex must be large in the range where the distance Ls is small and small in the range where the distance Ls is large. Since the shape of the sliding surface K described in FIG. 9 approaches a circle in a range where the hometown Ls is large, the shape of the outer edge portion of the sliding surface Kj is the shape of the sliding surface K described in FIG. It approximates the vortex line drawn by replacing the virtual circle Rsw shown.
In FIG. 26 (c), the position of the support shaft Sj that is provided at the link Aj and to which the start end portion Ns of the string N is attached is indicated by the arrow in the drawing around the support shaft Swj when the loading platform TA is fully raised. This is a position where the rotational moment due to the weight of the loading platform TA acting in the direction B and the rotational moment due to the pulling spring V are balanced.

As shown in FIG. 26 (c), the string N is in a straight line when the loading platform TA is fully raised. If a nail is driven into a point b that is in contact with the side surface of the straight string N that faces the support shaft Swj and that is close to the support shaft Swj, the loading platform TA is lowered slightly, and the link Aj rotates. The position b of the nail to be driven is a position where the straight string N is bent. The portion from the position b of the nail to the end portion Ne is a straight portion and is on the spring axis Zv.
When the string N is bent and the loading platform TA is stationary, the pulling spring V is extended, but the distance between the spring axis Zv and the support shaft Swj is decreased, and the pulling moment acting in the direction indicated by the arrow B in the figure is reduced. The rotational moment by the spring V is balanced.

Next, when the nail is newly driven into the point b that contacts the side surface of the linear portion of the string N facing the support shaft Swj and is close to the support shaft Swj, the loading platform TA is further lowered. When the link Aj further rotates, the position b of the nail to be newly driven is a position where the straight portion of the string N is bent. A portion extending from the position b of the nail to be newly driven to the terminal end Ne is a straight portion and is on the spring axis Zv.
When the string N is bent at the position b of a new nail and the loading platform TA is stationary, the tension spring V is further extended, but the distance between the spring axis Zv and the support shaft Swj is further reduced, and the weight is reduced. The rotational moment due to is balanced with the rotational moment due to the pulling spring V.

In this way, when new nails are sequentially driven, a sliding surface Kj around which the string N is wound is formed. The loading platform TA is stationary at an arbitrary height, with the rotational moment due to the weight balanced with the rotational moment due to the pulling spring V acting in the direction of arrow B in the figure.
If the link Av is swayed left and right from the stationary position and the attachment shaft Sv on the fixed support side of the tension spring V is moved, the loading platform TA can be raised or lowered.

26 (b) and 26 (c), the situation in which the position of the support shaft Sv does not change and the sliding surface Kj rotates around the support shaft Swj is shown in FIG. 26 (a). This is the same as the situation in which the position of the support shaft Sv rotates around the support shaft Swj without rotating around the support shaft Swj.
In FIG. 26A, the entire rotation range of the link Av is divided for the time being, and the position of the support shaft Sv corresponding to each rotation angle of the link Av divided for the time is a circle centered on the support shaft Swj. Arranged on Zhou Rswj for the time being.

The position of the nail that is sequentially driven in is represented by black dots painted black on the sliding surface Kj, and the interval between the black dots becomes narrower as it approaches the point Sj. The higher the link Av rises, the smaller the extension of the tension spring V with respect to the unit rotation angle of the link Av, and the smaller the increase in the distance between the spring axis Zv and the support shaft Swj. The increase in rotational moment due to the tension spring V is also small.
In this way, regardless of the weight of the load and regardless of the height of the loading platform TA, the moment of gravity and the force of the pulling spring V can be balanced, but the longer the pulling spring V, the pulling spring V The change in force is small, and the acceleration of the loading platform TA is reduced. In addition, the smaller the total rotation range of the link Av, the easier it is to stand the loading platform TA at an arbitrary height.

FIG. 27 relates to an elevator that is hung up and down on the pillar CL. The plate PL is attached to the elevator and moves up and down along the sliding surface K on the side of the pillar CL. A biasing means (not shown) acts on the plate PL, and the biasing means (not shown) is gravity acting in the direction of arrow B in the figure. The plate PL includes a prime mover that raises and lowers the lifted air, and the lift automatically releases the resistance that prevents the plate PL from falling. A force that urges the elevator in the falling direction and a resistance that resists and releases itself act on the elevator, and can stop and stop at any position of the column.

A wheel B, a drive gear Bm, and a driven gear Bg are mounted on each of the support shafts I provided on the plate PL, and the drive gear Bm is rotated by an electric motor. The plate PL descends along the column CL when rotating in the direction opposite to the arrow a in the figure.
In FIG. 27 (a), the drive gear Bm and the driven gear Bg are connected by a chain CH, and the chain CH is parallel to the sliding surface K of the side of the column CL and around each connection axis P of the chain CH. The “cam body Bk whose outer periphery is a spiral curve” is rotatably supported.

In FIG. 27B, the driven gear Bg2 and the driven gear Bg3 rotate in opposite directions, the driven gear Bg2 is directly connected to the drive gear Bm, and the driven gear Bg3 is connected to the drive gear Bm via the driven gear Bg3. The The driven gear Bg2 and the driven gear Bg3 have the same rotation shaft, and the wheel B2 and the wheel B3 are attached to each other, and a plurality of connecting shafts P are equally divided in the circumferential portions near the outer edge views of the wheels B2 and B3. The “cam body Bk whose outer periphery is a spiral curve” is rotatably supported around each of the connecting shafts P.

Each cam body Bk is equally divided, has the same shape and size, and the shape of the outer edge portion is the shape of the spiral curve described in FIG. 9B in which the distance from the connecting shaft P gradually increases or decreases. It is. When each cam body Bk moves along the sliding surface K with the force of the electric motor, and when each cam body Bk comes close to the sliding surface K both when the plate PL is raised and lowered, When the distance between the contact point b with the moving surface K and the connecting shaft P rotates and decreases while moving away from the sliding surface K, the distance between the contact point b and the connecting shaft P increases with increasing distance. .

When each cam body Bk descends along the sliding surface K due to gravity, the cam body Bk rotates in the direction of the arrow C in the figure while increasing the distance between the contact b and the connecting shaft P. In FIG. 27 (a), the distance between the support shaft I and the support shaft Ib is constant, and in FIG. 27 (b), the distance between the support shaft I2 and the support shaft I3 is constant. The force Fb that the moving surface K presses each cam body Bk is a force that rotates the cam body Bk in the direction opposite to the arrow C in the figure, and the more the cam body Bk rotates in the arrow C direction in the figure, And the connecting shaft P increases, and the pressing force Fb increases to resist the lowering of the plate PL.

The driven gear Bg supports the pressing force Fb. In FIG. 27A, the sliding surface Kb provided on the plate PL supports the pressing force Fb between the driving gear Bm and the driven gear Bg. In FIG. 27 (b), the frictional force acts between the sliding surface K and the chain Ch is fixed to the column CL. The drive gear Bm and the driven gear along the chain Ch fixed to the column CL. Bg goes up and down, and plate PL goes up and down.
In FIG. 27 (b), while the cam bodies Bk facing each other sandwich the column CL, the driven gear Bg2 and the driven gear Bg3 move up and down, and the plate PL moves up and down.

FIG. 28 illustrates a revolving door characterized by “a structure that can be retracted in the opening direction immediately before closing” so that fingers or a body is not caught between the door and the door. The door can be rotated so as to be retractable in the opening direction only in the range immediately before the door is closed, not in the range. In the figure, the alternate long and short dash line X indicates the wall core of the boundary wall, and N indicates the door frame.
When the body is sandwiched between the door D and the door frame N, there is no problem even if the door stops and remains stationary.

The pivot O is provided in the fixed portion W, and the door D is pivotally supported on the connection axis Cd of the plate PL that rotates about the pivot O. The plate PL is continuously rotated 360 degrees in the direction indicated by the arrow B in the figure by the force of an electric motor (not shown).
In order to explain in FIG. 28, the door D attached to the plate PL is assumed to be one. There are two positions where the door D sandwiches the body, the position where the door D crosses the boundary wall X.
The range immediately before the door D crosses the boundary wall X is the range (A), and the other is the range (A). The range (A) is the range where the door D is pivotally supported around the connection axis Cd, and the range (I) is the range where the door D is pivotally supported around the connection axis Cd. .

FIG. 28 (a) shows a state in which the door D rotates within the range of (A), and FIG. 28 (c) shows a state where the electric motor is stopped, the plate PL is stopped, and the door is stopped.
The rotating body J is rotatably supported around a connection shaft Cj provided on the plate PL, a wheel support shaft Ib is provided at the tip of the rotating body J, and a wheel B is mounted on the wheel support shaft Ib.
As shown in FIG. 28 (a), a recess Kd is provided on the side surface of the door D on the rotating shaft side, the rotating body J is urged by the push spring U, and the wheel B is fitted into the recess Kd. Press. The door D is fixed and supported at two points of the connection axis C and the contact point b of the recess Kd and the recess Kd. In a normal operation where the body is not sandwiched between the door D and the door frame N, the door D is fixed to the plate PL. It keeps rotating and rotates.

The sliding face K is pivotally supported around the pivot axis O, and the branch KA is attached thereto. The branch KA is urged by the pulling spring V and stops in a state where the contact Gk is pressed. The sliding face body K has two sliding faces K1 and K2 on the outer edge, and the two sliding faces K1 and K2 are along the circle centered on the pivot axis O, and the sliding face. The radius of the circle of K1 is larger than the radius of the circle of the sliding surface K2. The difference between the radius of the circle of the sliding surface K1 and the radius of the circle of the sliding surface K2 is equal to or larger than the diameter of the wheel B, the sliding surface K2 forms a recess K2, and the wheel B is accommodated in the recess K2. .
As shown in FIG. 28 (a), in a normal operation, the sliding surface K1 is provided in the range (A) and the sliding surface K2 is provided in the range (I). It is fixed to the fixed part W. When the wheel B moves along the sliding surface K1, the wheel B fitted in the recess Kd is sandwiched between the sliding surfaces K1 and cannot escape from the recess Kd. Cannot rotate around the connection axis Cd.

As shown in FIG. 28 (b), when the wheel B moves along the sliding surface K2, the wheel B fitted in the depression Kd is retracted from the depression Kd and can be accommodated in the depression K2. In the range of (ii), the door D can rotate in a direction opening around the connection axis Cd (in the direction of arrow A in the figure). When the wheel B passes through the range (i), the wheel B is in the depression Kd by the urging force of the push spring U during normal operation, and the door D does not rotate around the connecting shaft Cd.
As shown in FIG. 28 (b), in an emergency in which a body is sandwiched between the door D and the door frame N, a force that rotates the door D around the connection axis Cd in the direction of the arrow a in FIG. Thus, the wheel B moves along the sliding surface K door in the recess Kd, retracts from the recess Kd, and is accommodated in the recess K2. The pressing spring U contracts and the rotating body J rotates in the direction indicated by the arrow in FIG. As the wheel B moves away from the inside of the depression Kd, the door D rotates around the connection axis Cd. The force of sandwiching the body between the door D and the door frame N is eliminated, and a fatal accident can be avoided.

As shown in FIG. 28 (c), when the wheel B separated from the inside of the depression Kd moves along the sliding surface K2 and is locked to the end K2s of the sliding surface K2, the plate PL stops suddenly. The motor that rotates the PL stops its operation and brakes are applied. However, due to the dynamic inertia of the door, the plate PL rotates relative to the sliding face body K via the wheel B and rotates about the pivot O. to continue. The plate PL strikes away from the Gk, and the pulling spring V is stretched to absorb the dynamic inertia force of the door. Door D stops, and the electric motor continues to be braked, so the state where it is stopped continues.

A Link B Wheel C Connection shaft D Door b Contact G Contact H Height I Rotating shaft J Rotating body K Sliding surface L Length O Axis P Connecting shaft Q Bearing
R ratchet S moving body U push spring V tension spring W fixed part
Z orbit

Claims (2)

The moving body S that moves at a low speed, contacts and separates from the moving body D that moves at a high speed in the same direction, and decelerates the moving body D together with the moving body D biases the moving body D. The resistance that decelerates the moving body S, driven by power different from the means, acts on the moving body D through the contact b between the moving body D and the moving body S, and the contact b is a line of force acting through the contact b. And a speed reducer characterized by relatively moving in a substantially perpendicular direction. One container Sp1 and the other container Sp2 are spoids made of an elastic membrane that restores the volume of the fluid filled in the container Sp to a constant level, and are joined together by sharing the inlet / outlet Sl, without leaking from the inlet / outlet Sl. The other container Sp2 accommodates the fluid Fl discharged by the contraction of the container Sp1 while the other container Sp2 expands, and the fluid Fl accommodated in the other container Sp2 is returned to the one container Sp1, and the viscosity of the fluid Fl passing through the entrance / exit Sl A speed reducer characterized in that resistance resists expansion and contraction of one container Sp1 and the other container Sp2.

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