JP3019193B2 - Damper mechanism - Google Patents

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 A conventional damper mechanism of this type is disclosed in, for example, Japanese Patent Application Laid-Open No. 6-147249. The damper mechanism described in this publication has a casing having a storage hole, and a rotor rotatably inserted into the storage hole, and a gap between an inner peripheral surface of the storage hole and an outer peripheral surface of the rotor. An annular space is formed. A partition portion is formed on the inner peripheral surface of the storage hole so as to be rotatable relative to the outer peripheral surface of the rotor, and an opening / closing valve body is rotatably provided on the outer peripheral surface of the rotor. Then, the space is partitioned into a high-pressure chamber and a low-pressure chamber by the partition and the on-off valve body.

[0003] A valve portion protrudes from an outer peripheral surface of one side of the on-off valve body facing the high-pressure chamber. When the rotor rotates in one direction so that the volume of the high-pressure chamber decreases, the valve portion contacts the inner peripheral surface of the storage hole to shut off the space between the high-pressure chamber and the low-pressure chamber. When the rotor rotates in the other direction so as to increase, the high-pressure chamber and the low-pressure chamber communicate with each other while being separated from the inner peripheral surface of the storage hole.

Therefore, in the damper mechanism having the above structure, when the rotor rotates in one direction, a high pressure is generated in the high-pressure chamber, whereby rapid rotation in one direction is prevented, and the rotor rotates at low speed. Let me do. Conversely, when the rotor rotates in the other direction, no high pressure is generated in the high-pressure chamber and the low-pressure chamber. Therefore, the rotor can freely rotate.

[0005]

It is desirable that the valve portion be capable of immediately contacting the inner peripheral surface of the storage hole when the rotor starts rotating in one direction.
With such a configuration, when the rotor starts to rotate in one direction, it is possible to immediately prevent the rotor from rotating rapidly and rotate the rotor at a low speed. However, since the valve portion is relatively far away from the inner peripheral surface of the storage hole, it takes time to contact the inner peripheral surface of the storage hole, and as a result, rapid rotation of the rotor in one direction is immediately prevented. There was a problem that I could not do

[0006] If the distance between the valve portion and the inner peripheral surface of the storage hole is reduced, the valve portion can be brought into contact with the inner peripheral surface of the storage hole in a short time. The communication area between the high-pressure chamber and the low-speed chamber becomes small. For this reason, when the rotor rotates in the other direction, a small but damping action occurs, and free rotation of the rotor in the other direction is hindered.

[0007]

SUMMARY OF THE INVENTION The present invention has been made to solve the above problems, and the invention according to claim 1 has a casing having a storage hole and a relative rotation inside the storage hole of the casing. A rotor disposed movably, a fluid filled in an annular space formed between an outer peripheral surface of the rotor and an inner peripheral surface of the storage hole, and a rotatably provided on an outer peripheral surface of the rotor. An opening / closing valve body that partitions the space into a high-pressure chamber and a low-pressure chamber, and the opening / closing valve body is formed on one outer peripheral surface of the opening / closing valve body facing the high-pressure chamber by the pressure in the high-pressure chamber. When rotated in one direction, it comes into contact with the inner peripheral surface of the storage hole to shut off between the high-pressure chamber and the low-pressure chamber, and the pressure in the low-pressure chamber causes the on-off valve body to rotate in the other direction. When moved, the high-pressure chamber is separated from the inner peripheral surface of the storage hole. In a damper mechanism having a valve portion communicating with a pressure chamber, at least on the other side of the on-off valve body facing the low-pressure chamber, at least the valve portion is separated from an inner peripheral surface of the storage hole. An elastic piece is formed to abut the inner peripheral surface of the storage hole in an elastically deformed state, thereby urging the open / close valve body to rotate so that the valve portion approaches the inner peripheral surface of the storage hole. Features. in this case,
It is desirable that the elastic piece is always in contact with the inner peripheral surface of the storage hole.

[0008]

DESCRIPTION OF THE PREFERRED EMBODIMENTS A door closer using a damper mechanism according to the present invention will be described below as a preferred embodiment of the present invention with reference to FIGS. FIG.
As shown in FIG. 4, the door closer 1 is provided between the gate A and the gate B, and has a fixed part 2 fixed to the gate A and a rotating part 3 fixed to the gate B. are doing. The fixed portion 2 has a cylinder portion 2a, and a shaft 44 (described later) of the rotating portion 3 is rotatably inserted into the cylinder portion 2a, so that the rotating portion 3 is fixed to the fixed portion 2a. The gate B is rotatably supported by the gate A. Reference numeral C denotes a hinge provided between the gate post A and the gate B, and supports the gate B rotatably.

The door closer 1 includes a clutch mechanism 4 described later and a damper mechanism 5 according to the present invention.
With these functions, the gate B rotates as follows. That is, as shown in FIG.
It is rotatable between a closed position indicated by reference numeral A and a fully open position indicated by reference numeral C, and a range between the closed position A and a half-open position B separated by a predetermined rotation angle (hereinafter, this range) Is referred to as a regulation range X.), the return spring 45 of the clutch mechanism 4 urges the clutch mechanism 4 in the closing direction (the direction of the arrow B). Further, in the regulation range X, when the gate B is rotated in the opening direction (the direction of arrow A), the gate B is not rotated by the damper mechanism 5 but is rotated in the closing direction. At this time, a damper force acts to prevent rapid rotation of the gate B. On the other hand, in a range between the half-open position B and the fully-open position C (hereinafter, this range is referred to as a free range Y), the urging 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, in particular, 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 radially protruding from one side of the outer peripheral surface of the support tube portion 32. The rotation plate 3 is fixed to the gate B so that the rotating portion 3 It is fixed to the gate B. 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 in a lower portion of the inside of the support tube portion 32 of the rotating portion main body 31, and a damper mechanism 5 according to the present invention is provided in an upper portion. I have.

The clutch mechanism 4 applies a spring force in the closing direction to the gate B in the restriction range X and prevents the spring force from acting in the free range Y. , An intermediate cylinder 42, a gate-side fixed cylinder 43, a shaft body (rotor) 44, and a return spring 45 as main components.

The body-side fixed cylinder 41 is shown in FIGS.
As shown in the figure, the lower-diameter cylindrical portion 41a is concentric with the lower-diameter cylindrical portion 41b. The large-diameter cylindrical portion 41a is formed by fitting the key portion 41c into the key groove 34 of the support tubular portion 32.
Are fitted non-rotatably. A pair of locking window holes 41d, 41d are formed in the circumferential wall of the large-diameter cylindrical portion 41a in the circumferential direction.
° are arranged and formed apart. An insertion hole 41e extending in the circumferential direction is formed in the upper bottom of the large-diameter cylindrical portion 41a.

The intermediate cylinder 42 has a cylindrical shape, as shown in FIGS. 9 and 11, and is rotatably fitted to the inner peripheral surface of the large-diameter cylindrical portion 41a of the fixed cylinder 41. (See FIG. 7). A pair of locking grooves 42a are formed on the outer peripheral surface of the upper end portion of the intermediate cylinder 42 at a distance of 180 ° in the circumferential direction. A return spring 45 is provided on one of the pair of locking grooves 42a.
The locking claw 45a formed at the lower end of the main body side fixed cylinder 4
It fits through one insertion hole 41e. The upper end of the return spring 45 is supported by the support cylinder 32 of the rotating section main body 31 via the cylinder 11 (see FIG. 7). Then, the return cylinder 45 urges the intermediate cylinder 42 in the opening direction, and urges the rotating portion main body 31 in the closing direction. Since the fixed cylinder 41 is non-rotatably connected to the support cylinder 32 of the rotating section 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 42b at the upper end and a large-diameter hole 42c at the lower end. A pair of key grooves 42 is provided on the inner peripheral surface of the small diameter hole 42b.
d are formed 180 degrees apart in the circumferential direction. On the other hand, a pair of holding notches 42e penetrating through the large-diameter hole 42c is formed on the lower peripheral wall at the lower end side.
They are formed 0 ° apart. The holding notch 42e is formed in the locking window hole 4 of the 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 directed vertically. The outside diameter D of this clutch shaft 46 is
The width is substantially the same as the width 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.

If the outer diameter of the clutch shaft 46 is D, and the thickness of the peripheral wall of the intermediate cylinder 42 in which the holding notch 42e is formed is T, the following relationship holds: D> T. Therefore, the clutch shaft 46 is
The outer or inner part thereof projects from the holding notch 42e, and the holding notch 42e and the fixed cylinder 41
When the retaining window hole 41d is opposed to the
Part of the outside of the clutch shaft 46 protruding from e can enter the locking window hole 41d. In a state where a part of the clutch shaft 46 has entered the locking window hole 41d, the intermediate cylinder 42 and the fixed cylinder 41 are non-rotatably connected via the clutch shaft 46.

The outer diameter D of the clutch shaft 46 is D / 2
<T. Moreover, the holding notch 42e
Assuming that 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 of the large-diameter cylindrical portion 41a. Therefore, the clutch shaft 46 enters the engagement window hole 41d only in a portion smaller than half of the entire clutch shaft 46. Therefore, if it is attempted to relatively rotate the fixed cylinder 41 and the intermediate cylinder 42 in a state where a part of the clutch shaft 46 has entered 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 end side small diameter portion 43a and a lower end side large diameter portion 43b which are concentric with each other. The small diameter portion 43a is rotatably fitted in the large diameter hole 42c of the intermediate cylinder 42. On the other hand, a substantially square projecting portion 43c is formed on the lower end surface of the large diameter portion 43b. One end of the connection fitting 12 is non-rotatably fitted to the protruding portion 43c, and two engagement pieces 1 are attached to the other end of the connection fitting 12.
2a and 12b are formed. Then, as shown in FIG. 4, by inserting the fixing portion 2 between the engagement pieces 12a and 12b, the connection fitting 12 is non-rotatably connected to the fixing portion 2, and the gate-side fixing cylinder 43 is eventually turned. It is non-rotatably connected to the fixed part 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 ° 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. In addition, the locking groove 43d has the same radius of curvature as the clutch shaft 46, and the protrusion amount P
And has substantially the same depth. Therefore, the locking groove 4
When 3d faces the holding notch 41e, a part of the inside of the clutch shaft 46 can enter the locking groove 43d. When the clutch shaft 46 is partially inserted, the fixed cylinder 43 and the intermediate cylinder 42 are non-rotatably connected via the clutch shaft 46. If the fixed cylinder 43 and the intermediate cylinder 42 are relatively rotated in this state, the clutch shaft 46 is pushed outward by one of the two side edges of the locking groove 43d.

Next, the operation of the clutch mechanism 4 having the above configuration will be described. In this case, the positional relationship among the locking window 41d, the holding notch 42e, and the locking groove 43d will be clear. Now, it is assumed that the gate B is located at the closed position A. At this time, as shown in FIG. 13A, a part of the inside 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 so that the locking window hole 41d is separated from the holding notch 42e of the intermediate member 42 in the closing direction (the direction of arrow B), and is urged in the closing direction by the return spring 45. I have. Therefore, the gate B is also biased in the closing direction.

When the gate B is turned in the opening direction against the urging force of the return spring 45, the fixed cylinder 41 is also turned in the same direction. Then, when the gate B is rotated to the half-open position B, as shown in FIG. 13B, the locking window hole 41d faces the holding notch 42e. Thereafter, when the fixed cylinder 41 is further rotated in the same direction, the intermediate cylinder 42 is urged in the opening direction by the return spring 45 as shown in FIG. The outer edge of the clutch shaft 46 is pushed out by the locking groove 43d, and a part of the outer side enters the locking window hole 41d. Thereby, while the connection between the intermediate cylinder 42 and the gate-side fixed cylinder 43 is released, 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 rotate freely and can stop at any position. Then, as shown in FIG.
Is rotated to the fully open position c, it cannot be further rotated. This will be described later.

Conversely, when the gate B is rotated from the fully closed position C toward the closed position A when the gate B is rotated to the half open position B, the fixed cylinder 41 rotates in the same direction. The holding notch 42e faces the locking groove 43d. Thereafter, when the fixed cylinder 41 is further rotated in the closing direction by a small 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 falling out of the locking window hole 41d, a part of the inside enters the locking groove 43d. As a result, the connection between the fixed cylinder 41 and the intermediate cylinder 4 is released, and the intermediate cylinder 42 and the fixed cylinder 43 are non-rotatably connected. Therefore, the urging force in the closing direction by the return spring 45 acts on the fixed cylinder 41, and the gate B is closed and rotated to the closed position A by the return spring 45.

In the free range Y, the gate B
Can be freely rotated, so that it can be rapidly rotated in the closing direction. However, when the gate B is rapidly rotated from the free range Y to the restricted range X, the clutch shaft 46 does not enter the locking groove 43d at the half-open position B, but 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 of this embodiment employs 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 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 this shaft body 44,
A pair of key grooves 44a, 44a are arranged 180 degrees apart in the circumferential direction, and approximately half 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. Thus, 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 on the inner peripheral surface of the gate-side fixed cylinder 43. Each rotation restricting groove 43
e extends in the circumferential direction by substantially the same angle as the angle between the half-open position A and the fully-open position C, and the lower half of the key 47 is fitted movably in the circumferential direction. In addition, when the gate B closes from the fully open position C and reaches the half open position B, the key 47 is turned into the rotation restricting groove 43e.
e, when it abuts against the end 47f on the closing direction side and rotates open from the half-open position B to reach the fully open position c, the other end 47g.
It is arranged so that it may 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 and the holding notch 42e faces the locking groove 43d of the fixed cylinder 43,
Since the key 47 abuts on the end 47f, the key 47 cannot rotate further in the same direction and stops. Therefore,
The clutch shaft 46 can reliably enter there without passing through the locking groove 43d. When the gate B rotates in the opening direction and reaches the fully open position c, the key 46 is moved to the regulating groove 4.
Since the intermediate cylinder 42 and the shaft body 44 cannot rotate any more in the same direction because of abutment against the end portion 47g of 3e, the intermediate cylinder 42 and the shaft body 44 stop. As a result, the gate-side fixed cylinder 41 and the main body 31 are stopped, and the gate B is reliably stopped 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 comprises a pressure generating section 6 and a pressure control section 7. There are features of the present invention.

First, the pressure generator 6 will be described.
The pressure generating section 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, the main body 31 has a cylindrical shape.
And the key portion 6.
The support cylinder 1b is non-rotatably supported by fitting the key 1b into the key groove 34 of the support cylinder 32. Therefore, the casing 61 rotates integrally with the gate B. The shaft body 44 is provided at the center of the housing hole 61a of the casing 61.
Are inserted into the shaft 44, as shown in FIGS.
As shown in FIGS. 15 and 16, a large-diameter portion 44 b is formed at a location facing the casing 61. Between the outer peripheral surface of the large diameter portion 44b and the inner peripheral surface of the casing 61, an annular closed space whose upper and lower ends are sealed by seal members 62, 62 is formed. A fluid is sealed in this closed space. It is desirable to use a viscous fluid as the fluid.

On the inner peripheral surface of the housing hole 61a, two partition portions 61c are arranged and formed 180 ° apart in the circumferential direction. The distal end surface (the inner peripheral surface) of each partition 61c is the shaft 4
The outer space 4 is rotatably and liquid-tightly contacted with the outer peripheral surface of the housing 4, thereby dividing 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 180 ° apart in the circumferential direction. On the tip end surface (surface on the outer peripheral side) of each support ridge 44c,
A substantially semicircular supporting recess 44d is formed. The opening / closing valve body 63 is rotatably supported in each support recess 44d.

The opening / closing valve body 63 cooperates with the partition wall 61c to open the space S in an opening rotation direction (arrow A in FIG. 15).
A high pressure chamber S _H direction) side is for partitioned into a low-pressure chamber S _L of the closed kinematic direction (arrow B direction) side, and has a shaft portion 63a which forms a substantially circular cross section. The opening / closing valve body 63 is rotatably supported by the shaft body 44 by the shaft part 63a being rotatably fitted into the support recess 44d. On one side of the outer peripheral surface of the shaft portion 63a in the direction of arrow A, a valve portion 63b is formed which extends over the entire length thereof. Further, a valve portion 63 is provided on an outer peripheral surface of the on-off valve body 63.
From the point slightly shifted in the direction of arrow B from the tip of b, the shaft 6
A communication groove 63c extending to 3a is formed.

By the valve portion 63b and the communication groove 63c,
Depending on the rotational direction of the gates B and the the high-pressure chamber S _H and the low-pressure chamber S _L so that the communication is interrupted. That is, FIG.
5 (A) shows a state when the gate B is closed. When the gate B is opened from the closed position a and the casing 61 is turned in the direction of arrow A accordingly (at this time, 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 separates 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, high pressure is not generated in the high pressure chamber S _H and the low-pressure chamber S _L.

On the other hand, FIG. 15B shows a state in which the gate B is located at the half-open position B. From this state, the gate B is closed and rotated, and the casing 61 is moved in accordance with the arrow B in response thereto. When rotated in the direction, the valve body 63 by the fluid in the high pressure chamber S _H is pivoted in the counterclockwise direction, the valve portion 63b is in 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 is cut off, a high pressure is generated in the high pressure chamber S _H. When the high pressure chamber _SH becomes high pressure, the pressure presses the casing 61 in the opening direction via the partition 61c. Therefore, the gate B closes and turns at a low speed. The pressure in the high pressure chamber S _H is adjusted appropriately by the pressure control unit 7 to be described later.

Here, in the damper mechanism 5 of the present invention, when the casing 61 starts to rotate in the direction of arrow A, the valve portion 63b is brought into immediate contact with the inner peripheral surface of the storage hole 61a. The following configuration is adopted. That is, as shown in FIG. 1 and FIG.
On the outer peripheral surfaces of both ends of the shaft portion 63a, elastic pieces 63d projecting in the opposite direction to the valve portion 63b are formed. When the elastic piece 63d is elastically deformed, the distal end thereof has a storage hole 61d.
By pressing and contacting the inner peripheral surface of a, the valve portion 63b is rotationally urged to approach the inner peripheral surface of the storage hole. In this embodiment, the elastic piece 63d is provided with the storage hole 61.
a is always in pressure contact with the inner peripheral surface of the storage hole 661a, but it is sufficient that at least the valve portion 63b is in press contact with the inner peripheral surface of the storage hole 661a when the valve portion 63b is away from the storage hole 61a. As shown by the imaginary line in FIG.
When d is in contact with the inner peripheral surface of the storage hole 61a,
It may be formed so as to be separated from the inner peripheral surface of the storage hole 61a.

In the damper mechanism 6 in which the elastic piece 63d is formed, the valve portion 63b is moved by the urging force of the elastic piece 63d to the inner periphery of the storage hole 61a except when the casing 61 is rotated in the direction of arrow B. It is brought into pressure contact with the surface. Therefore, when to rotate the casing 61 in the arrow B direction, it can generate high pressure almost simultaneously the high pressure chamber S _H and turning start.

As shown by the imaginary line in FIG.
When the valve portion 63b is in contact with the inner peripheral surface of the storage hole 61a, even when the elastic piece 63d is configured to be separated from the inner peripheral surface of the storage hole 61a, the casing 6
1 is rotated in the direction of arrow A, the elastic piece 63d is in press contact with the inner peripheral surface of the storage hole 61a. Therefore, when the rotation in the same direction is interrupted, the elastic piece 63d becomes the valve portion 63b. Are moved closer to the storage holes 61a to reduce the distance between them. Thus, the casing 61 begins to rotate in the direction of arrow B, can be contacted in a short time the valve portion 63b on the inner peripheral surface of the accommodation hole 61a, is possible to immediately generate a high pressure in the high pressure chamber S _H it can.

Further, since the elastic piece 63d is elastically deformable, the opening / closing valve body 63 can rotate clockwise against the urging force of the elastic piece 63d, and the casing 61 rotates in the direction of arrow A. At times, the valve portion 63d can be sufficiently separated from the inner peripheral surface of the storage hole 61a. Therefore, free rotation of the casing 61 in the direction of arrow A is not hindered.

When the gate B is located in the free area X between the half-open position B and the fully-open position C, the casing 61 and the shaft 44 rotate integrally. Therefore, high pressure is not generated in the high pressure chamber S _H.

Next, the pressure controller 7 will be described.
As shown in FIGS. 18 and 19, a vertical hole 44e extending downward is formed in the upper end surface of the shaft body 44. An upper horizontal hole 44e and a lower horizontal hole 44f are formed in the large diameter portion 44b. Upper lateral hole 44e has one end opened to the low pressure chamber S _L, the other end is vertical hole 44e open. On the other hand, the lower horizontal hole 44g has one end open to the high pressure chamber S _H, and the other end is open to the vertical hole 44e.

A pressure regulating valve 8 is provided in the vertical hole 44e. The pressure adjusting valve 8 has a valve body 81 screwed into the vertical hole 44e. The lower end of this valve body 81
The storage hole 81a is located slightly above the lower horizontal hole 44g, and has a storage hole 81a extending upward at the center of the lower end surface. The valve body 81 has window holes 81b, 81b extending from the outer peripheral surface to the storage hole 81a. Each window hole 81b is arranged and formed so as to communicate with the upper horizontal hole 44f regardless of the rotational position of the valve body 81.

A valve element 82 is slidably provided in the storage hole 81a. At the lower end of the valve body 82, a valve portion 82a is formed. This valve portion 82a is connected to the high pressure chamber S
Until _H reaches a predetermined pressure, it is pressed against the bottom surface of the vertical hole 44e by a spring 83 for urging the valve body 82 downward, and protrudes downward from the storage hole 81a. The urging force of the spring 83 can be adjusted by adjusting the amount of screwing of the adjusting screw 84. A plurality of vertically extending communication grooves 8 are provided on the outer peripheral surface of the valve body 82 following the valve portion 82a.
2b is formed. The communication groove 82b is
In the state where a abuts against the bottom surface of the vertical hole 44e,
The lower end is exposed downward from the vertical hole 44e, and the upper end is
1b. Therefore, in this state, the upper edge and the valve body 81 of the high pressure chamber S _H and the low-pressure chamber S _L tricuspid portion 82a
Are communicated with each other through a gap C between the lower end edge of the first member, the communication groove 82b, the window hole 81b, and the upper and lower horizontal holes 44f and 44g. Meanwhile, moves upward against the urging force of the valve portion 82a spring 83, when fitted into the accommodating hole 81a, are blocked by the high pressure chamber S _H and the low-pressure chamber S _L leaflets 82.

The pressure control unit 7 configured as described above, to adjust the pressure in the high pressure chamber S _H as follows, to control the closed kinematic velocity of the gates B. That is, when the gates B starts closed kinematic in regulating range X by the biasing force of the return spring 45, the fluid is lower horizontal hole 44g in the high pressure chamber S _H, the clearance C, the communication groove 82b, windows 8
Through 1b and upper lateral holes 82b and flows into the low pressure chamber S _L. At the beginning of the closing rotation in which the rotation speed of the gate B is slow, the flow resistance to the fluid due to the gap C is small, but as the closing rotation speed of the gate B increases, the flow resistance in the gap C increases. There is no closing rotation at a speed higher than the rotation speed.
The flow resistance due to the gap C can be adjusted by changing the position of the valve body 81 in the vertical direction.

[0043] In the course closed movement of the gates B, when it is pressed in the closing direction by the wind or manpower, but gates B tries closed kinematic above a predetermined speed, the pressure in the high pressure chamber S _H The valve body 82 moves upward against the urging force of the spring 83, and the valve portion 82a fits into the storage hole 81a. Thus, the cut off between the high pressure chamber S _H and the low-pressure chamber S _L. Therefore, the gate B stops. In practice, the partition wall 61 of the large diameter portion 44b and the casing 61 of the high pressure chamber gaps minute between the members for blocking between S _H and the low-pressure chamber S _L, for example, shaft 44
Since the fluid flows through the small gap between the gate B and the gate B, the gate B closes and turns at an extremely low speed. When the pressing force in the closing direction to gates B does not act, the pressure of the high pressure chamber S _H is lowered, is moved downward by the valve body 82 the spring 83. Thus, communication with the high pressure chamber S _H and the low-pressure chamber S _L again, gates B is closed kinematic again at a predetermined rotational speed.

As shown in FIG. 8, the clutch mechanism 4 and the damper mechanism 5 are attached to the supporting cylindrical portion 32 by upper and lower lids 13 and 14 so as not to escape. Reference numeral 15 denotes a decorative lid.

The damper mechanism according to the present invention is not limited to the above-described embodiment, and can be appropriately designed and changed. For example,
In the above embodiment, the damper mechanism according to the invention is applied to a door closer, but this damper mechanism can also be applied to, for example, a supporting device that rotatably supports a toilet lid.

[0046]

As described above, according to the first aspect of the present invention, when the casing and the rotor are relatively rotated so that the volume of the high-pressure chamber is reduced, the relative rotation is immediately started. The valve portion can be brought into contact with the inner peripheral surface of the storage hole in a short time, whereby a high pressure can be immediately generated in the high pressure chamber. In addition, when the casing and the rotor are relatively rotated in the opposite directions, the valve portion can be sufficiently separated from the inner peripheral surface of the storage hole, and therefore, a damper force acts upon the relative rotation in the same direction. Can be prevented. According to the second aspect of the present invention, a high pressure can be generated in the high-pressure chamber almost simultaneously with the relative rotation of the casing and the rotor so that the volume of the high-pressure chamber is reduced.

[Brief description of the drawings]

FIG. 1 is an enlarged cross-sectional view showing a main part of a damper mechanism according to the present invention, and FIG. 1 (A) shows a state where a valve portion is separated from an inner peripheral surface of a casing, and FIG. ) Shows a state when the valve portion is in contact with the inner peripheral surface of the casing.

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

FIG. 3 is a perspective view showing an attachment 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 rotation unit.

FIG. 8 is a view showing a rotating portion main body of the rotating portion, and FIG.
8A is a front view thereof, FIG. 8B is a plan view thereof, FIG.
FIG. 9C is a sectional view taken along the line CC of FIG.

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

10 (A) is a plan view, FIG. 10 (B) is a front view thereof, and FIG. 10 (C) is FIG. 10 (A). It is CC sectional drawing of.

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

12 (A) is a plan view, FIG. 12 (B) is a front view thereof, and FIG. 12 (C) is a bottom view thereof. 12 (D) is a sectional view taken along line DD of FIG. 12 (A).

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

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

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

16 (A) is a partially omitted front view, FIG. 16 (B) is a partially omitted side view, and FIG. 16 (C) is a view showing a shaft body of the door closer. CC of (B)
FIG. 16D is a cross-sectional view, FIG.
(F) is EE and FF sectional drawing of FIG. 16 (A), respectively.

17A and 17B are diagrams showing an opening / closing valve body of a pressure generating portion of a damper mechanism of the door closer, wherein FIG. 17A is a plan view thereof, and FIG. 17B is a BB enlarged view of FIG. 17A. Sectional view,
FIG. 17C is a view as seen from the arrow C in FIG. 18B.

FIG. 18 is a view illustrating a pressure control unit of the damper mechanism shown in FIG.
It is a Z enlarged sectional view.

FIG. 19 is an exploded perspective view showing the pressure control unit.

[Explanation of symbols]

S _H high pressure chamber S _L low-pressure chamber 1 door closer 5 damper mechanism 6 pressure generating portion 44 the shaft (rotor) 61 casing 61a accommodating hole 61c partition wall 63 opening-closing valve body 63a shaft portion 63b valve portion 63d elastic piece

──────────────────────────────────────────────────続 き Continued on front page (58) Field surveyed (Int.Cl. ⁷ , DB name) F16F 9/14 E05F 3/14 E05F 3/20

Claims (2)

(57) [Claims] 1. A casing having a storage hole, a rotor disposed rotatably in the storage hole of the casing, and a rotor formed between an outer peripheral surface of the rotor and an inner peripheral surface of the storage hole. A fluid filled in an annular space; and an opening / closing valve body rotatably provided on an outer peripheral surface of the rotor and dividing the space into a high-pressure chamber and a low-pressure chamber. On one side outer peripheral surface of the valve body, the high-pressure chamber and the low-pressure chamber contact the inner peripheral surface of the storage hole when the on-off valve body is rotated in one direction by the pressure in the high-pressure chamber. And a valve unit for communicating between the high-pressure chamber and the low-pressure chamber apart from the inner peripheral surface of the storage hole when the on-off valve body is rotated in the other direction by the pressure in the low-pressure chamber. The other side of the on-off valve body facing the low-pressure chamber. When at least the valve portion is away from the inner peripheral surface of the storage hole, the valve portion abuts on the inner peripheral surface of the storage hole in an elastically deformed state, so that the valve portion contacts the inner peripheral surface of the storage hole. A damper mechanism comprising: an elastic piece for urging the on-off valve body to rotate so as to approach the damper mechanism. 2. The damper mechanism according to claim 1, wherein said elastic piece is always in contact with an inner peripheral surface of said storage hole.