JPH0942352A - Damper mechanism - Google Patents

Abstract

PROBLEM TO BE SOLVED: To communicate high and low pressure chambers with each other rapidly after push-press force acted on the high pressure chamber is released, and shorten a door closing time, by forming a valve part on a valve hole to engage freely and remove freely, in a damper mechanism which is suitable in a door closer and the like, and in which a valve part is opened/closed by differential pressure between the high and low pressure chambers. SOLUTION: A damper mechanism 5 for a door closer is constituted of a pressure generating part 6 and a pressure control part 7, a valve body is rotated by a fluid in a low pressure chamber SL in the case where a door is opened and a casing 61 is rotated in the pressure generating part 6, it is apart from a housing hole, and thereby, a high pressure chamber SH is communicated with a low pressure chamber SL. When the door is closed, the housing hole is shut off by the valve body so as to generate damper effect. In the pressure control part 7, a valve part 82a is pushed to the bottom surface of a vertical hole 44e by a spring 83 till pressure in the high pressure chamber SH exceeds a prescribed pressure. In the case of prescribed pressure or more, a valve body 82 is moved upward opposing to the spring 83, a clearance between the valve body 82 and the valve main body 81 is reduced so as to increase circulating resistance.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a damper mechanism suitable for use in a door closer or the like.

[0002]

2. Description of the Related Art Generally, a door closer is provided with a damper mechanism for preventing the door from closing and rotating at high speed. As such a damper mechanism, for example, Japanese Unexamined Patent Publication No. Hei 4
There is one described in Japanese Patent Publication No. 27090. The damper mechanism includes a valve body movably arranged in a valve hole that connects the high pressure chamber and the low pressure chamber, and an elastic member that urges the valve body from the low pressure chamber side toward the high pressure chamber side. A valve seat is formed at the opening of the valve hole on the high pressure chamber side. On the other hand, the valve body has a valve portion formed at an end portion protruding from the valve hole toward the high pressure chamber. This valve portion is normally separated from the valve seat, but when the pressure difference between the high pressure chamber and the low pressure chamber exceeds a predetermined value,
The differential pressure allows the valve seat to be seated.

The damper mechanism having the above-described structure prevents the high-speed closing and rotation of the door as follows. That is, when the door is closed and rotated, the fluid in the high pressure chamber enters the valve hole through the gap between the opening of the valve hole on the high pressure chamber side and the valve portion, and further flows into the low pressure chamber from the valve hole. To do. Here, when the fluid passes through the gap between the opening portion of the valve hole and the valve portion, a flow resistance is generated, and the closing resistance of the door is suppressed to a low speed by the flow resistance. Moreover, a differential pressure is generated between the high pressure chamber and the low pressure chamber based on the flow resistance, and the differential pressure increases as the closing and rotating speed of the door increases. When the differential pressure exceeds a predetermined value, the differential pressure causes the valve element to move closer to the valve hole against the biasing force of the elastic member. Then, the gap between the valve hole and the valve portion becomes smaller, and the inflow amount of the fluid from the high pressure chamber to the low pressure chamber is further restricted. As a result, the closing rotation speed of the door is suppressed to a lower speed. After that, when the differential pressure further increases and exceeds a predetermined value defined by the elastic member, the valve portion sits on the valve seat and closes the valve hole. This stops the door.

[0004]

In the above-mentioned conventional damper mechanism, when the differential pressure greatly exceeds the predetermined value defined by the elastic member, the force acting on the door is removed and then the door is closed again. There was a problem that it took time to start turning. That is, once the valve portion is seated on the valve seat, the high pressure chamber is sealed. Therefore, the high pressure chamber should maintain a high pressure and the valve portion should continue to be seated. However, in reality, when the force acting on the door is removed, the fluid in the high pressure chamber flows out of the slight gap existing between the members partitioning the high pressure chamber and the low pressure chamber and then flows into the low pressure chamber. Then, when the pressure becomes equal to or lower than a predetermined pressure, the elastic member separates the valve portion from the valve seat, and the valve hole is opened again. Therefore, the door starts to close and rotate again. However, when the pressure in the high pressure chamber is significantly higher than the predetermined pressure, it takes a relatively long time from when the valve portion is seated on the valve seat until the pressure in the high pressure chamber falls below the predetermined pressure. . For this reason, there has been a problem that it takes time for the door to restart the closing rotation.

[0005]

In order to solve the above-mentioned problems, the invention according to claim 1 has a valve portion facing a high pressure chamber side opening of a valve hole for communicating the high pressure chamber with the low pressure chamber. Have,
A valve body movably arranged in the axial direction of the valve hole so that the valve section approaches and separates from the opening section of the valve hole, and urges the valve body so that the valve section separates from the valve hole. A damper mechanism comprising an elastic member, wherein the valve portion is moved toward and away from an opening portion on the high pressure chamber side of the valve hole by a pressure difference between the high pressure chamber and the low pressure chamber, and the valve portion is provided with the valve hole. Mated to,
It is characterized by being formed so as to be detachable.

[0006]

BEST MODE FOR CARRYING OUT THE INVENTION A door closer employing a damper mechanism according to the present invention will be described below as a preferred embodiment of the present invention with reference to FIGS. Figure 2
As shown in FIG. 4, the door closer 1 includes a gate post A and a gate B.
And a fixed portion 2 which is provided between
And a rotating portion 3 fixed to the gate B. The fixed portion 2 has a cylinder portion 2a, and the shaft portion 44 of the rotation portion 3 is rotatably inserted into the cylinder portion 2a, so that the rotation portion 3 is freely rotated by the fixed portion 2. The gate B is rotatably supported by the gate post A. Reference numeral C is a hinge provided between the gate post A and the gate B, and rotatably supports the gate B.

The door closer 1 is, as will be described later,
The clutch mechanism 4 and the damper mechanism 5 according to the present invention are provided, and the gate B is rotated as follows by these mechanisms 4 and 5. That is, as shown in FIG. 5, the gate B is rotatable between a closed position indicated by reference sign a and a fully open position indicated by reference sign c, and is separated from the closed position a by a predetermined rotation angle. Range between half-open position b (hereinafter,
This range is called the regulation range X. ), The return spring 45 of the clutch mechanism 4 causes the closing direction (arrow B direction).
Has been energized. Further, in this regulation range X,
When the gate B is rotated in the opening direction (arrow A direction), the damper force by the damper mechanism 5 does not act on the gate B, but when the gate B is rotated in the closing direction, the gate B rapidly rotates. A damper force that prevents movement is applied. On the other hand, in the range between the half open position (b) and the fully open position (c) (hereinafter, this range is referred to as the free range Y), the biasing force and the damper force do not act on the gate B, and the gate B rotates freely. , Can be stopped.

Next, the structure of the door closer 1, particularly the structure of the rotating portion 3, will be described in detail. As shown in FIG. 7, the rotating portion 3 has a rotating portion main body 31. As shown in FIG. 8, the rotating portion main body 31 has a cylindrical support tubular portion 32.
And a mounting plate portion 33 that radially projects from one side of the outer peripheral surface of the support tubular portion 32. By fixing the mounting plate portion 33 to the gate B, the rotating portion 3 is provided. It is fixed to the gate B. Further, a key groove 34 extending from the upper end to the lower end is formed on the inner peripheral surface of the support cylinder 32.

As shown in FIG. 7, a clutch mechanism 4 is provided on the lower side and a damper mechanism 5 according to the present invention is provided on the upper side inside the support tubular portion 32 of the rotating portion main body 31. There is.

The clutch mechanism 4 is for applying a spring force in the closing direction to the gate B in the regulation range X and preventing the spring force from acting in the free range Y. The intermediate cylinder 42, the gate side fixed cylinder 43, the shaft body 44 and the return spring 45 are the main constituent elements.

The main body side fixed cylinder 41 is shown in FIG. 9 and FIG.
As shown in FIG. 5, it is composed of a large-diameter cylindrical portion 41a on the lower end side and a small-diameter cylindrical portion 41b on the upper end side which is concentric with the large-diameter cylindrical portion 41a. The large-diameter cylindrical portion 41a is fitted with the key portion 41c into the key groove 34 of the support tubular portion 32, whereby the support tubular portion 32 is
It is fitted so as not to rotate. A pair of locking window holes 41d and 41d are provided in the circumferential wall portion of the large-diameter cylindrical portion 41a in the circumferential direction by 180 degrees.
° Placed apart. Further, an insertion hole 41e extending in the circumferential direction is formed in the upper bottom portion of the large-diameter cylindrical portion 41a.

As shown in FIGS. 9 and 11, the intermediate cylinder 42 has a cylindrical shape and is rotatably fitted to the inner peripheral surface of the large-diameter cylindrical portion 41a of the fixed cylinder 41. (See Figure 7). On the outer peripheral surface of the upper end portion of the intermediate cylinder 42, a pair of locking grooves 42a are formed at 180 ° apart in the circumferential direction. A return spring 45 is provided in one of the pair of locking grooves 42a.
The locking claw 45a formed at the lower end of the
It fits in through the first insertion hole 41e. The upper end portion of the return spring 45 is supported by the support tubular portion 32 of the turning portion main body 31 via the tubular body 11 (see FIG. 7). Then, the return spring 45 urges the intermediate cylinder 42 in the opening direction, while urging the turning portion main body 31 in the closing direction. Since the fixed cylinder 41 is non-rotatably connected to the support cylinder portion 32 of the rotating portion main body 31, the fixed cylinder 41 is also urged in the closing direction by the return spring 45.

The intermediate cylinder 42 has a small-diameter hole portion 42b on the upper end side and a large-diameter hole portion 42c on the lower end side therein. A pair of key grooves 42 is formed on the inner peripheral surface of the small diameter hole portion 42b.
d are arranged and formed 180 degrees apart in the circumferential direction. On the other hand, the peripheral wall portion on the lower end side that defines the large-diameter hole portion 42c is provided with a pair of holding cutout portions 42e penetrating therethrough in the circumferential direction.
They are formed 0 ° apart. The holding notch 42e is provided with the locking window hole 4 of the main body side fixed cylinder 41 in the axial direction.
It is arranged at the same position as 1d.

A cylindrical clutch shaft 46 is inserted into the holding notch 42e with its axis oriented in the vertical direction. The outer diameter D of the clutch shaft 46 is equal to the holding notch 42.
It is almost the same as the width of e (width in the circumferential direction).
Therefore, the clutch shaft 46 cannot move in the circumferential direction of the intermediate cylinder 42, but can move in the radial direction.

Further, assuming that the outer diameter of the clutch shaft 46 is D and the thickness of the peripheral wall portion of the intermediate cylinder 42 in which the holding notch portion 42e is formed is T, there is a relation of D> T. Therefore, the clutch shaft 46 is
A part of the outer side or the inner side projects from the holding cutout portion 42e, and the holding cutout portion 42e and the fixed cylinder 41
The holding notch 42
A part of the outer side of the clutch shaft 46 protruding from e can enter the locking window hole 41d. The intermediate cylinder 42 and the fixed cylinder 41 are non-rotatably connected via the clutch shaft 46 when a part of the clutch shaft 46 enters the locking window hole 41d.

The outer diameter D of the clutch shaft 46 is D / 2.
<It has a relationship of T. Moreover, the holding notch 42e
When the amount of protrusion of the clutch shaft 46 from P is P (= D−T), the amount of protrusion P is substantially the same as the thickness of the peripheral wall portion of the large diameter cylindrical portion 41a. Therefore, the clutch shaft 46 enters the locking window 41d only in a portion smaller than half of the entire clutch shaft 46. Therefore, if the fixed cylinder 41 and the intermediate cylinder 42 are attempted to rotate relative to each other in a state where a part of the clutch shaft 46 enters the locking window hole 41d,
The clutch shaft 46 is pushed inward by one of the inner side edges of the locking window hole 41d.

As shown in FIGS. 7, 9 and 12, the gate side fixed cylinder 43 has an upper small diameter portion 43a and a lower large diameter portion 43b which are concentric with each other. The small diameter portion 43a is rotatably fitted in the large diameter hole portion 42c of the intermediate cylinder 42. On the other hand, a substantially square-shaped protruding portion 43c is formed on the lower end surface of the large diameter portion 43b. This protrusion 4
One end of the connecting fitting 12 is non-rotatably fitted to the 3c, and two engaging pieces 12 are attached to the other end of the connecting fitting 12.
a, 12b are formed. Then, as shown in FIG. 4, the fixing member 2 is inserted between the engaging pieces 12a and 12b so that the connecting fitting 12 is non-rotatably connected to the fixing member 2, and the gate side fixing cylinder 43 is fixed. It is non-rotatably connected to the fixed portion 2.

On the outer peripheral surface of the small diameter portion 43a of the fixed cylinder 43, a pair of locking grooves 43d, 43d are formed 180 degrees apart in the circumferential direction. The locking groove 43d is arranged at the same position as the holding notch 41e of the intermediate cylinder 42 in the axial direction. Moreover, the locking groove 43d has the same radius of curvature as the clutch shaft 46, and the protrusion amount P
It has almost the same depth as. Therefore, the locking groove 4
When 3d faces the holding notch 41e, a part of the inner side of the clutch shaft 46 can enter the locking groove 43d. The fixed cylinder 43 and the intermediate cylinder 42 are non-rotatably connected to each other via the clutch shaft 46 when the clutch shaft 46 is partly inserted. Further, if the fixed cylinder 43 and the intermediate cylinder 42 are attempted to rotate relative to each other in this state, the clutch shaft 46 is pushed outward by one of both side edges of the locking groove 43d.

Next, the operation of the clutch mechanism 4 having the above structure will be described. The positional relationship among the locking window 41d, the holding notch 42e, and the locking groove 43d will be clarified by this. It is assumed that the gate B is now in the closed position a. At this time, as shown in FIG. 13A, a part of the inner side of the clutch shaft 46 has entered the locking groove 43d, and the intermediate cylinder 42 and the fixed cylinder 43 are non-rotatably connected. Further, the fixed cylinder 41 is positioned such that the locking window hole 41d is separated from the holding notch 42e of the intermediate member 42 in the closing direction (direction of arrow B), and is biased in the closing direction by the return spring 45. There is. Therefore, the gate B is also biased in the closing direction.

When the gate B is rotated in the opening direction against the biasing force of the return spring 45, the fixed cylinder 41 is also rotated in the same direction. Then, when the gate B is rotated to the half open position (b), the locking window hole 41d faces the holding notch 42e as shown in FIG. 13 (B). Thereafter, when the fixed cylinder 41 is further rotated in the same direction, the intermediate cylinder 42 is biased in the opening direction by the return spring 45 as shown in FIG. It is pushed outward by the side edge of 43d, a part of the inner side of the clutch shaft 46 comes out of the engagement groove 43d, and a part of the outer side enters the engagement window hole 41d. As a result, the connection between the intermediate cylinder 42 and the gate-side fixed cylinder 43 is released, while the fixed cylinder 43 and the intermediate cylinder 42 are integrally connected. As a result,
The biasing force of the return spring 45 acting between the fixed cylinder 41 and the intermediate cylinder 42 is received by the clutch shaft 46,
It does not act as a force to close the gate B. Therefore,
The gate B can freely rotate and can be stopped at any position. Then, as shown in FIG. 13 (D), the gate B
When is rotated to the fully open position c, it cannot be rotated further open. This point will be described later.

On the contrary, when the gate B is pivoted to the half-open position B when it is pivoted from the fully closed position C side to the closed position B side, the fixed cylinder 41 is rotated in the same direction. The holding cutout portion 42e faces the locking groove 43d. After that, when the fixed cylinder 41 is further rotated in the closing direction by a slight amount, it is pushed inward by the side edge of the locking window hole 41d located in the opening rotation direction. As a result, the clutch shaft 46 moves inward,
While coming out of the locking window hole 41d, a part of the inside enters into the locking groove 43d. As a result, the fixed cylinder 41 and the intermediate cylinder 4 are disconnected, and the intermediate cylinder 42 and the fixed cylinder 43 are non-rotatably connected. Therefore, a biasing force of the return spring 45 in the closing direction acts on the fixed cylinder 41, and the return spring 45 causes the gate B to be closed and rotated to the closed position B.

By the way, in the free range Y, the gate B
Since it can be freely rotated, it can be rapidly rotated in the closing direction. However, when the gate B is rapidly rotated from the free range Y to the restriction range X, the clutch shaft 46 does not enter the locking groove 43d at the half-open position B, but the locking groove 43d remains in the locking window hole 41d. May pass through. In order to prevent such a problem and to surely stop the gate B at the fully open position C, the door closer 1 has the following configuration.

That is, as shown in FIG. 7, the inner diameter of the small diameter portion 41b of the main body side fixed cylinder 41, the inner diameter of the small diameter hole portion 42b of the intermediate cylinder 42, and the inner diameter of the gate side fixed cylinder 43 are set to the same size. The shaft body 44 is inserted through them. On the outer peripheral surface of the shaft body 44,
A pair of key grooves 44a, 44a are formed so as to be spaced apart by 180 ° in the circumferential direction, and approximately half of the inside of the key 47 is fitted into each key groove 44a. The upper half of the outer half of the key 47 is fitted into the key groove 42d of the intermediate cylinder 42. As a result, the shaft body 44 and the intermediate cylinder 42 are connected so as to rotate integrally.

As shown in FIGS. 12 and 13, a pair of rotation restricting grooves 43e, 43e are formed in the upper portion of the inner peripheral surface of the gate side fixed cylinder 43. Each rotation restriction groove 43
The letter e extends in the circumferential direction by an angle substantially equal to the angle between the half open position a and the fully open position c, and the lower half of the key 47 is fitted in the circumferential direction so as to be movable. Moreover, when the gate B is closed and rotated from the fully open position C side to reach the half open position B, the rotation restricting grooves 43e are moved by the keys 47.
When it hits the end 47f on the side of the closing direction of e and turns open from the half open position B side to reach the fully open position c, the other end 47g.
It is arranged so as to hit.

Therefore, the intermediate cylinder 42 and the shaft body 44
Is rotated in the direction of arrow B from the fully open position C side, and when the holding notch 42e faces the locking groove 43d of the fixed cylinder 43,
Since the key 47 hits the end portion 47f, the key 47 can no longer rotate in the same direction and the key 47 stops. Therefore,
The clutch shaft 46 can surely enter there without passing through the locking groove 43d. Further, when the gate B rotates in the opening direction to reach the fully open position C, the key 46 is moved by the key 46.
Since it hits the end portion 47g of 3e, the intermediate cylinder 42 and the shaft body 44 can no longer rotate in the same direction and stop. As a result, the gate-side fixed cylinder 41 and the main body portion 31 stop, and eventually the gate B stops at the fully open position C.

Next, the damper mechanism 5 according to the present invention will be described. As shown in FIG. 7, the damper mechanism 5 is composed of a pressure generating section 6 and a pressure control section 7, and the pressure control section 7 includes There is a characteristic part of this invention.

First, the pressure generator 6 will be described.
The pressure generator 6 has a casing 61 and the shaft body 44 as main components. The casing 61 is shown in FIGS.
As shown in FIG. 15 and having a storage hole 61a therein, it has a cylindrical shape.
Is fitted to the inner periphery of the support tubular portion 32 of the
By fitting 1b into the key groove 34 of the support tubular portion 32, it is non-rotatably supported by the support tubular portion 32. Therefore, the casing 61 rotates together with the gate B. The shaft body 44 is inserted through the central portion of the housing hole 61 a of the casing 61. This shaft body 44 has a structure shown in FIGS.
4 and FIG. 16, a large diameter portion 44b is formed at a position facing the casing 61.
Between the outer peripheral surface of 4b and the inner peripheral surface of the casing 61, an annular closed space whose upper and lower ends are sealed by the seal members 62, 62 is formed. A fluid is enclosed in this closed space. It is desirable to use a viscous fluid as the fluid.

On the inner peripheral surface of the accommodation hole 61a, two partition wall portions 61c are arranged and formed 180 degrees apart in the circumferential direction. The tip end surface (the surface on the inner peripheral side) of each partition wall portion 61c is the shaft 4
The outer peripheral surface of 4 is in a relatively rotatable manner and is in liquid-tight contact, thereby partitioning the closed space into two spaces S, S.
On the other hand, on the outer peripheral surface of the large-diameter portion 44b of the shaft body 44, two support protrusions 44c are arranged and formed at 180 ° apart in the circumferential direction. On the tip end surface (surface on the outer peripheral side) of each support protrusion 44c,
A support recess 44d having a substantially semicircular cross section is formed.
The opening / closing valve body 63 is rotatably supported in each of the support recesses 44d.

The on-off valve body 63 cooperates with the partition wall 61c to open the space S in the high pressure chamber S _H on the side of the open rotation direction (direction of arrow A in FIG. 14) and the close rotation direction (direction of arrow B). ) Side low pressure chamber S _L, and has a shaft portion 63a having a substantially circular cross section as shown in FIGS. 14, 15 and 17. The shaft portion 63a is rotatably fitted in the support recess 44d, so that the shaft body 4
4 rotatably supported. A valve portion 63b extending over the entire length is formed on one side of the outer peripheral surface of the shaft portion 63a on the arrow A direction side. In addition, a communication groove 63c is formed on the outer peripheral surface of the opening / closing valve body 63 and extends from the tip of the valve portion 63b to a position slightly closer to the arrow B direction to the shaft portion 63a.

Due to the valve portion 63b and the communication groove 63c,
The high pressure chamber S _H and the low pressure chamber S _L communicate with each other and are shut off depending on the rotating direction of the gate B. That is, FIG.
5 (A) shows a state when the gate B is closed, and the gate B is opened and rotated from the closed position a, and the casing 61 is rotated in the arrow A direction in response thereto (at this time, as described above). As described above, the shaft body 44 is stopped.), The low pressure chamber S _L
The valve body 63 is rotated clockwise by the fluid inside,
The valve portion 63b moves away from the inner peripheral surface of the storage hole 61a. As a result, the high pressure chamber S _H and the low pressure chamber S _L communicate with each other through the communication groove 63c. Therefore, no high pressure is generated in the high pressure chamber S _H and the low pressure chamber S _L.

On the other hand, FIG. 15 (B) shows a state in which the gate B is located at the half open position (b), and the gate B is rotated in the closed state from that state, and the casing 61 is correspondingly indicated by the arrow B. When the valve body 63 is rotated in the direction, the valve body 63 is rotated counterclockwise by the fluid in the high pressure chamber S _H , and the valve portion 63b comes into contact with the inner peripheral surface of the casing 61. As a result, the high pressure chamber S
_H and the low pressure chamber S _L are cut off, and a high pressure is generated in the high pressure chamber S _H. The high-pressure fluid in the high-pressure chamber S _H flows into the low-pressure chamber S _L via the pressure control unit 7, as will be described later.

Elastic projecting pieces 63d projecting in the opposite direction to the valve part 63b are formed at both upper and lower ends of the shaft part 63a. The elastic projection piece 63d has a tip portion inside the storage hole 61a when the valve body 63 is rotated clockwise by the rotation of the casing 61 in the arrow A direction to open the communication groove 63c. The peripheral surface is pressed and elastically deformed, and the valve body 63 is urged to rotate counterclockwise. Therefore, when the casing 61 rotating in the direction of the arrow A is stopped, the elastic protruding piece 63d rotates the valve body 63 counterclockwise to bring the valve portion 63b closer to the inner peripheral surface of the storage hole 61a. Therefore, when the casing 61 is rotated in the direction of the arrow B, the valve portion 63 comes into immediate contact with the inner peripheral surface of the storage hole 61a, and high pressure can be immediately generated in the high pressure chamber S _H. .

The gate B has a half open position b and a fully open position c.
The casing when located in the free area X between
61 and the shaft body 44 rotate integrally. Therefore, high pressure
Room S _HNo high pressure is generated in

Next, the pressure control section 7 according to the present invention will be described. As shown in FIGS. 1 and 18, a vertical hole 44e extending downward is formed in the upper end surface of the shaft body 44. Further, an upper lateral hole 44e and a lower lateral hole 44f are formed in the large diameter portion 44b. Upper horizontal hole 44e
Has one end opened to the low pressure chamber S _L and the other end opened to the vertical hole 44e. On the other hand, one end of the lower horizontal hole 44g is opened to the high pressure chamber S _H , and the other end is opened to the vertical hole 44e.

A pressure adjusting valve 8 is provided in the vertical hole 44e. The pressure regulating valve 8 has a valve body 81 screwed into the vertical hole 44e. The lower end of the valve body 81 is
A storage hole (valve hole) 81a extending upward is formed at the center of the lower end surface of the lower horizontal hole 44g at substantially the same position as the upper inner peripheral surface thereof. Also, the valve body 8
1 has a window hole 8 extending from the outer peripheral surface thereof to the storage hole 81a.
1b and 81b are formed. Each window hole 81b is arranged and formed so as to communicate with the upper lateral hole 44f of the valve body 81.

A valve body 82 is slidably provided in the storage hole 81a. The valve portion 8 is provided at the lower end of the valve body 82.
2a is formed, and this valve portion 82a has a storage hole 81a.
The storage hole 81a is closed by fitting into the storage hole 81a, and the storage hole 81a is opened by exiting from the storage hole 81a. Further, a plurality of communication grooves 82b extending vertically are formed on the outer peripheral surface of the valve body 82 continuing to the upper side of the valve portion 82a.
Are formed.

The valve body 82 is urged downward by a spring 83, and the valve portion 82a escapes downward from the storage hole 81a until the pressure in the high-pressure chamber S _H reaches a predetermined pressure, and the vertical hole is formed. It is pressed against the bottom surface of 44e. In this state, the high pressure chamber S _H and the low pressure chamber S _L have a clearance C between the upper end edge of the valve portion 82a and the lower end edge of the valve body 81, and the communication groove 8
2b, the window hole 81b, and the upper and lower lateral holes 44f and 44g. Of course, when the valve portion 82a moves upward against the biasing force of the spring 83 and fits into the storage hole 81a,
The high pressure chamber S _H and the low pressure chamber S _L are shut off by the valve body 82. The biasing force of the spring 83 can be adjusted by adjusting the screwing amount of the adjusting screw 84.

The pressure control unit 7 having the above-mentioned structure adjusts the pressure of the high pressure chamber S _H as follows, and controls the closing and rotating speed of the gate B. That is, when the gates B to closed kinematic by the biasing force of the return spring 45 in the regulating range X, the fluid is lower horizontal hole 44g in the high pressure chamber S _H, the clearance C, the communication groove 82b, window holes 81b
And flows into the low pressure chamber S _L via the upper lateral hole 82b. Here, a resistance is generated when the fluid passes through the clearance C, and the closing rotation speed of the door B is suppressed to a low speed by this flow resistance. In other words, high pressure is generated in the high pressure chamber S _{H due} to the flow resistance, and the rotation speed of the gate B is suppressed to a low speed by the pressure. This pressure is small when the gate B is rotating at a low speed, but increases when the gate B is rotating at a high speed according to the rotation speed of the gate B. Then, when the pressure in the high pressure chamber S _H further increases, the pressure causes the valve body 82 to move upward against the biasing force of the spring 83. As a result, the size of the clearance C is reduced, and the flow resistance of the clearance C is increased. Therefore, the closing and rotating speed of the gate B is suppressed to a low speed. The size of the gap C can be adjusted by changing the position of the valve body 81 in the vertical direction.

When the gate B is strongly pushed by the wind or manpower and it is attempted to close and rotate at a higher speed, the high pressure chamber S
The pressure in _H causes the valve body 82 to move upward against the biasing force of the spring 83, and the valve portion 82a fits into the housing hole 81a. Then, the valve body 82 stops at a position where the pressing force due to the pressure of the high pressure chamber S _{H and} the urging force of the spring 83 are balanced. When the valve body 82 stops, the gate B also stops.

After that, when the pressing force in the closing direction on the gate B ceases to act, the gate B is slightly rotated in the opening direction by the spring back of the fluid, and the pressure in the high pressure chamber S _H is slightly lowered. Then, the valve body 8 due to the pressure in the high pressure chamber S _H
Since the pressing force against 2 is smaller than the urging force of the spring 83, the valve body 82 is moved downward. Accordingly
The gate B is further rotated in the opening direction. Here, when the valve body 82 moves downward, the urging force of the spring 83 decreases accordingly. Therefore, the valve body 82 stops when the urging force of the spring 83 and the pressing force of the high pressure chamber S _H balance, The gate B should also stop, but once the gate B rotates in the opening direction, the gate B continues to rotate further due to its inertia and the biasing force of the spring 83, and the valve body 82 continues to move downward. Then, the valve portion 82a of the valve body 82 escapes downward from the storage hole 44e. Then, the fluid in the high pressure chamber S _H begins to flow out again to the low pressure chamber S _L , and the gate B starts to rotate again.

As described above, in the damper mechanism 5 of the present invention, after the pressing force in the closing direction on the gate B is no longer applied, the damper mechanism 5 is slightly rotated in the opening direction by the urging force of the spring 83, and then immediately closed. To resume. Therefore, the time until the closed rotation is restarted can be significantly reduced.

As shown in FIG. 7, the clutch mechanism 4 and the damper mechanism 5 are fixed to the supporting cylindrical portion 32 by the upper and lower lids 13 and 14 so as not to be able to escape. Further, reference numeral 15 is a makeup lid.

The damper mechanism of the present invention is not limited to the above-mentioned embodiment, but the design can be changed appropriately. For example, this embodiment applies the damper mechanism according to the invention to a door closer, but this damper mechanism can also be applied to a support device that rotatably supports a lid of a toilet bowl, for example.

[0044]

As described above, according to the invention of claim 1, it is possible to prevent the fluid in the high pressure chamber from flowing out to the low pressure chamber from between the partition wall portion and the shaft body. The damper effect can be exerted more reliably, and since it is not necessary to improve the processing accuracy of the inner peripheral surface of the partition wall portion, the manufacturing cost can be reduced.

[Brief description of drawings]

1 is a ZZ enlarged cross-sectional view of FIG. 7 showing a main part of a damper mechanism according to the present invention, FIG. Fig. 1 (B)
Shows the state when the valve portion is fitted in the housing hole.

FIG. 2 is a front view showing a gate pillar and a gate to which a door closer using the damper mechanism according to the present invention is attached.

FIG. 3 is a perspective view showing a mounting state of a door closer, a gate post, and a gate.

FIG. 4 is a plan view of the same.

FIG. 5 is a plan view showing a rotation range of a gate.

FIG. 6 is a perspective view showing a rotating portion of the door closer.

FIG. 7 is a vertical cross-sectional view of the rotating portion.

FIG. 8 is a diagram showing a rotating portion main body of the rotating portion, and FIG.
8A is its front view, FIG. 8B is its plan view, and FIG.
FIG. 8C is a sectional view taken along line CC of FIG.

FIG. 9 is an exploded perspective view showing a clutch mechanism of the door closer.

FIG. 10 is a view showing a main body side fixed cylinder of the clutch mechanism, FIG. 10 (A) is a plan view thereof, FIG. 10 (B) is a front view thereof, and FIG. 10 (C) is a view of FIG. 10 (A). It is CC sectional drawing of.

FIG. 11 is a view showing an intermediate cylinder of the clutch mechanism, FIG. 11 (A) is a plan view thereof, FIG. 11 (B) is a front view thereof, FIG. 11 (C) is a bottom view thereof, and FIG. Figure D)
It is the DD sectional view of 1 (A).

FIG. 12 is a view showing a gate side fixed cylinder of the clutch mechanism, FIG. 12 (A) is a plan view thereof, FIG. 12 (B) is a front view thereof, and FIG. 12 (C) is a bottom view thereof. 12D is a cross-sectional view taken along the line D-D of FIG.

13 is an enlarged cross-sectional view taken along line XX of FIG.
(A) shows the state when the gate is located at the closed position, FIG. 13 (B) shows the state when the gate is located at the half open position, and FIG. 13 (C) shows the gate at the half open position. 13 (D) shows a state when it is slightly rotated from the position to the fully open position.
Shows the state when the gate is in the fully open position.

FIG. 14 is an exploded perspective view showing a pressure generating portion of the damper mechanism of the door closer.

15 is an enlarged cross-sectional view taken along line YY of FIG. 7 showing the pressure generating portion, FIG. 15 (A) shows a state in which the gate is in the closed position, and FIG. 15 (B) shows The state when the gate is located in the half open position is shown.

16 is a view showing a shaft body of the door closer, FIG. 16 (A) is a partially omitted front view thereof, FIG. 16 (B) is a partially omitted side view thereof, and FIG. (B) CC
A cross-sectional view, FIG. 16D is a plan view thereof, FIG.
16F is a cross-sectional view taken along line EE and FF of FIG.

FIG. 17 is a diagram showing an opening / closing valve body of a pressure generating portion of the damper mechanism of the door closer, FIG. 17 (A) is a plan view thereof, and FIG. Cross section,
17C is a view taken in the direction of arrow C in FIG. 17B, and FIG.
FIG. 4 is an enlarged cross-sectional view showing the relationship between the inner peripheral surface of the casing and the on-off valve body.

FIG. 18 is an exploded perspective view showing a pressure control unit of the damper mechanism.

[Explanation of symbols]

C clearance S _H high pressure chamber S _L low-pressure chamber 1 door closer 5 damper mechanism 7 the pressure controller 8 pressure regulating valve 81 valve body 81a accommodating hole (valve hole) 82 valve 82a valve 83 spring (elastic member)

Claims (1)

[Claims] 1. A valve portion facing a high-pressure chamber-side opening of a valve hole that connects the high-pressure chamber and the low-pressure chamber to each other. A valve body disposed so as to be movable in the axial direction, and an elastic member for urging the valve body so that the valve portion separates from the valve hole, and the valve portion includes the high pressure chamber and the low pressure chamber. A damper mechanism in which the valve portion is brought into and out of contact with the opening of the valve hole on the high pressure chamber side by a pressure difference between the valve hole and the valve hole so that the valve portion can be fitted into and removed from the valve hole.