JPH09177858A - Hinge damper - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a hinge damper to change a suppression force according to the opening closing speed of a body to be opened and closed. SOLUTION: A hinge damper comprises a damping force generating mechanism to intercommunicate first and second chambers 12 and 13 and generate a damping force when the difference pressure of oil liquid between the first and second chambers 12 and 13 exceeds a given pressure; and movement converting mechanisms 39 arranged at a cover part on the second chamber 13 side and a partition member 14 and converting rotation of the partition member 14 into axial movement. When the opening speed of a door is increased, a flow of oil liquid is throttled by a notch 43 to generate a damping force, and when the opening speed of the door is further increased, a pressure applied on a valve element 42 is increased, the valve element 42 is bent and a communication passage 40 is opened according to an oil pressure to generate a damping force. A suppression force having a strength proportioning to the opening speed of a door is exerted on the door by a damping force by a notch 3, a damping force by the valve element 42, or a damping force by the notch 43 and the valve element 42, and rapid opening of the door is prevented from occurring.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a hinge damper used for opening and closing a door or the like of a refrigerator.

[0002]

2. Description of the Related Art An example of a conventional hinge damper is disclosed in Japanese Utility Model Publication No. 7-20428. The hinge damper shown in the publication is configured by enclosing viscous grease in the clearance between the fixed member and the rotating member.
When the object to be opened and closed such as the door connected to the rotating member rotates, the rotating force acts as a shearing force on the viscous grease, and the rotating member overcomes the viscous resistance and rotates. As a result, a part of the external force applied to the object to be opened and closed is absorbed by the viscous grease to suppress the rotational speed of the object to be opened and closed.

[0003]

By the way, in the hinge damper, when the opening / closing speed of the object to be opened / closed is small, the restraining force for the opening / closing speed of the object to be opened / closed may be small, but when the opening / closing speed is high, the impact force is alleviated. Therefore, it is desirable to obtain a large suppression force. However, in the above-described conventional technology, the speed is simply suppressed by using the shearing force of viscous grease, and the size of the suppressing force corresponding to the opening / closing speed cannot be obtained, and the above-mentioned demand cannot be satisfied. It was

The present invention has been made in view of the above circumstances, and an object of the present invention is to provide a hinge damper capable of changing the restraining force according to the opening / closing speed of an object to be opened / closed.

[0005]

According to the first aspect of the present invention,
A tubular member having a lid on both ends and having an oil liquid sealed inside,
A shaft provided in the tubular member and extending to the outside from at least one lid portion of the tubular member; and a shaft housed in the tubular member and integrally rotatably engaged with the shaft. It is provided so as to be movable in the axial direction with respect to the shaft,
A defining member that defines the inside of the tubular member into first and second chambers;
A damping force generating mechanism that communicates the first and second chambers and generates a damping force when the differential pressure of the oil liquid between the first and second chambers exceeds a predetermined pressure; A spring member interposed between the first chamber side lid portion and the second chamber side lid portion side to press the defining member toward the second chamber side lid portion side; And a motion conversion mechanism that converts the rotation of the defining member into a motion in the axial direction.

According to the structure of claim 1, when the defining member rotates, the defining member linearly moves toward the first chamber or the second chamber by the operation of the motion converting mechanism, and the first and second chambers move. Due to the pressure difference between the two chambers, the oil liquid flows through the damping force generating mechanism.

In the structure according to the first aspect of the present invention, the motion conversion mechanism includes a first inclined surface formed on an opposing surface of the defining member facing the lid portion side of the second chamber side, and a second chamber side. May be formed on a facing surface of the lid portion facing the defining member side, and may include a second inclined surface that matches the first inclined surface.

According to a first aspect of the present invention, the motion conversion mechanism includes a first inclined surface formed on a facing surface of the partition member facing the lid portion side of the second chamber side, and a second chamber side. A second inclined surface that is formed on an opposing surface of the lid portion that faces the defining member side, and that coincides with the first inclined surface, the first inclined surface, and the second inclined surface.
The inclined surfaces may be formed so as to coincide with each other in the middle of the circumferential direction and have a flat surface having a predetermined length in the circumferential direction.

In the structure according to any one of claims 1 to 3, the lid portion on the first chamber side may be constructed so that the insertion depth can be adjusted with respect to the tubular member.

[0010]

DETAILED DESCRIPTION OF THE INVENTION A hinge damper according to a first embodiment of the present invention will be described below with reference to FIGS.
In FIG. 1, the tubular member 2 of the hinge damper 1 has one end side,
First and second lids 3 and 4 are provided on the other end side to enclose the oil liquid inside, and a tubular member side bracket 5 is provided on both end sides.

The first and second lid portions 3 and 4 are fitted to the tubular member 2 via the seal members 6 and 6, and the first and second caps 7 and 8 are attached to the inner wall of the tubular member 2. Formed annular groove 9,
Retaining rings 10 and 10 (see FIG. 10) fitted to 9, and washers 11 and 11 (see FIG. 9) interposed between the retaining rings 10 and 10 and the first and second caps 7 and 8. And the first and second caps 7 and 8 are washers 11 and 11.
It is supported by the retaining rings 10 and 10 via, and is prevented from coming off.

As shown in FIG. 10, the retaining ring 10 has a substantially ring-like shape with an end and has a force that spreads radially outward. A jig hole 10a is formed at the end of the retaining ring 10. The retaining ring 10 is assembled in the annular groove 9 of the tubular member 2 in this state by inserting a jig (not shown) into the jig hole 10a to bring both ends closer to each other to reduce the diameter. Inside the tubular member 2, as shown in FIG.
As shown in FIG. 12, a defining member 14 that defines the inside of the tubular member 2 into first and second chambers 12 and 13 is housed.
The defining member 14 has a shape in which the outer peripheral portion is along the inner wall of the tubular member 2, and is rotatable and linearly movable with respect to the tubular member 2.

A spring member 17 is interposed between the defining member 14 and the first cap 7 via a thrust bearing 15 and a spring bearing 16, and the defining member 14 is located on the second cap 8 side. Is pressed against. Thrust bearing 15
Prevents the rotational movement of the defining member 14 from being transmitted to the spring member 17.

A shaft 18 is inserted through the defining member 14. The shaft 18 is a shaft body 19 having a predetermined diameter.
And the first and second extension shafts 20 having a smaller diameter than the shaft main body 19 connected to the ends of the shaft main body 19,
21 and 21. In the vicinity of the second extension shaft 21 of the shaft main body 19, as shown in FIGS. 1 and 7, a flat plate portion (hereinafter, referred to as main body side flat plate portion) 22 is formed by two-way cutting.
Are formed. The portion of the shaft body 19 in which the main body side flat plate portion 22 is formed is inserted into a hole 23 formed in the defining member 14 and having a shape along the main body side flat plate portion 22, whereby the defining member 14 is formed. Is movable in the axial direction along the shaft 18, and the defining member 14
And the shaft 18 are fixed in the rotation direction, and the force in the rotation direction is transmitted to the other side (that is, the force in the rotation direction is exchanged between the defining member 14 and the shaft 18). .

The first extension shaft 20 includes a spring bearing 16 and a first
The second extension shaft 21 also projects to the outside through the cap 7, the washer 11, and the retaining ring 10, and the second extension shaft 21 also protrudes to the outside through the second cap 8, the washer 11, and the retaining ring 10. In the present embodiment, the first cap 7, the washer 11, and the retaining ring 10 form a lid on the first chamber side, and the second cap 8, the washer 11, and the retaining ring 10 are the second. Constitutes a lid portion on the room side.

As shown in FIGS. 6 and 7, a flat plate portion (hereinafter referred to as the first and second extension shaft flat plate portions) is formed on the outer protruding portions of the first and second extension shafts 20 and 21 by two-way cutting. 2)
4 and 25 are formed, and the flat plate portions 24 and 25 are shown in FIG.
As shown in FIG. 3, the door side bracket 27 fixed to the door (opening / closing member) 26 is engaged with the mounting portion of the door side bracket 27 so as to be surely fixed.

As shown in FIG. 1, the second cap 8 has a substantially columnar cap body 28 which is fitted to the tubular member 2 and is prevented from coming off by the washer 11 and the retaining ring 10, and the cap body 28. Grooves 2a formed on the tubular member 2 that are formed on the member 14 side and have a ring shape in plan view (hereinafter, referred to as an inclined tubular portion) 29 and the cap body 28 that face each other (see FIG. 5). ), And a pair of protrusions 30 that prevent the cap body 28 and the second cap 8 from rotating.
30 (see FIG. 8).

As shown in FIGS. 4 and 1, the facing surfaces of the inclined tubular portion 29 facing the defining member 14 extend in the direction orthogonal to the tubular member 2 and face each other at a constant length in the circumferential direction. A pair of flat surfaces (hereinafter, referred to as cap-side flat surfaces) 31 and 31 having an arcuate shape in a plan view, and a pair of flat surfaces 31 and 31 that are connected to the ends of the flat surfaces 31 and 31 and are substantially perpendicular to the direction orthogonal to the tubular member 2. It is composed of inclined surfaces (hereinafter, referred to as cap side inclined surfaces) 32 and 33 which are inclined in the same direction and which are arcuate in plan view.
In this case, the cap-side inclined surface 32 is concave as compared with the cap-side flat surface 31, and the cap-side inclined surface 33
Is more convex than the cap-side flat surface 31. Here, the inclined surfaces 32 and 33 form a second inclined surface.

As shown in FIGS. 2 and 3, the defining member 14 has a substantially cylindrical defining member body 34 along the inner wall of the tubular member 2.
It is composed of a tubular abutting member 35 which is formed on the second cap 8 side of the defining member main body 34 and has a ring shape in plan view. As shown in FIGS. 2 and 3, the facing surface of the contact member 35 facing the second cap 8 side extends in a direction orthogonal to the tubular member 2 and faces each other at a constant length in the circumferential direction. Flat surface (hereinafter, referred to as the defining member side flat surface) 3
6, 36 and a pair of the defining member side flat surfaces 36, 36, which are connected to the ends of the defining member side flat surfaces 36, 36 and are convex and concave with respect to the defining member side flat surface 36 in substantially the same direction as the direction orthogonal to the tubular member 2. And an inclined surface (hereinafter, referred to as a defining member side inclined surface) 37, 38 having a substantially arcuate shape in a plan view.

In this case, the defining member side inclined surface 37 is more convex than the defining member side flat surface 36, and the defining member side inclined surface 38 is on the defining member side flat surface 36. It is concave in comparison. Here, the inclined surfaces 37 and 38 constitute a first inclined surface. Then, as shown in FIG. 1, the contact member 35 has the defining member-side flat surface 36 and the defining member-side inclined surfaces 37 and 38, respectively, as shown in FIG. The inclined surfaces 32 and 33 are opposed to and in contact with the opposed surfaces of the inclined cylindrical portion 29 over the entire circumference. In the present embodiment, the defining member side flat surface 36, the abutting member 35 having the defining member side inclined surfaces 37 and 38 formed therein, and the cap side flat surface 31, and the inclined cylinder having the cap side inclined surfaces 32 and 33 formed therein. The part 29 is the motion conversion mechanism 3
9.

The partition member body 34 includes a first chamber 1 and a second chamber 1.
A plurality of communication passages 40 for communicating the Nos. 2 and 13 are shown in FIGS.
As shown in FIG. A plurality of ring-shaped flexible valve bodies 42, which are inserted into the shaft 18, are provided in the opening portion of the communication passage 40 on the second chamber 13 side so as to face the communication passage 40 and are stacked. . Furthermore, the valve body 4
A spring 45 is interposed between the spring 2 and the cap body 28 via a spring receiver 44, and presses the valve element 42 against the opening of the communication passage 40 with a predetermined pressure. As shown in FIG. 11, a notch 43 is formed in the valve body 42 that comes into contact with the defining member main body 34. The notch 43 and the communication passage 4 are formed.
The first and second chambers 12, 13 communicate with each other via 0. The notch 43 is adapted to generate a damping force when the differential pressure of the oil liquid between the first and second chambers 12 and 13 becomes a predetermined pressure or more, and further, when the differential pressure becomes large, the pressure becomes Accordingly, the valve body 42 bends and the opening area of the communication passage 40 changes, so that the damping force can be adjusted. In the present embodiment, the damping force generating mechanism is formed by the notch 43, the communication passage 40, the valve body 42 arranged so as to face the communication passage 40, and the spring 45 for adjusting the opening area of the communication passage 40 via the valve body 42. It is configured.

The hinge damper 1 is attached to the door mechanism 46 as shown in FIG. In FIG.
The door mechanism 46 includes a door support 47 and the door 26 rotatably supported by the door support 47 via the hinge damper 1. The tubular member 2 is attached to the door support 47 by fixing the tubular member side bracket 5 with bolts 48. A door-side bracket 27 is attached to the door 26 with bolts 48. The door 26 is rotatably supported by the door support body 47 via the hinge damper 1 by fitting the first and second extension shaft flat plate portions 24, 25 into the door side bracket 27. Here, the door side bracket 27 is fitted to the first and second extension shaft flat plate portions 24 and 25 as shown in FIG. 1 when the door 26 is closed, as shown in FIG.
End surface (defining member side flat surface 36, defining member side inclined surface 3
7, 38) is the end surface of the inclined tubular portion 29 (the cap-side flat surface 3).
1, the cap-side inclined surfaces 32, 33) are set so as to match and abut over the entire circumference. Further, as shown in FIG. 12, the defining member side inclined surface 37 is formed on the cap side inclined surface 33.
With a portion of the doors facing each other, the door 26 has a desired amount (for example, 15
0 °) Set to open.

Hinge damper 1 constructed as described above
Then, when the door 26 is rotated in the opening direction from the state shown in FIG. 1, the shaft 18, and thus the defining member 14 is rotated by its rotational force, and when the door 26 is rotated by a predetermined angle, the defining member 14 is rotated. The state shown in FIG. 12 (the door 26 is in a desired amount and is open) is obtained. By this rotation, the defining member 14 is
The top portion 37a of the defining member-side inclined surface 37 is guided by the cap-side inclined surface 32 and the cap-side inclined surface 33 against the spring force of the spring member 17, and at the same time the first chamber is opened at a speed corresponding to the opening speed of the door 26. It moves linearly toward the 12 side (upward in FIG. 1). When the partition member 14 moves to the first chamber 12 side, the oil liquid passes from the first chamber 12 to the second chamber 12 through the communication passage 40 and the notch 43.
Flows into the chamber 13.

At this time, while the opening speed of the door 26 is low,
The oil passes through the notch 43 without receiving resistance, while the door 2
When the opening speed of 6 is increased, the flow of the oil liquid is throttled by the notch 43 to generate a damping force, and when the opening speed of the door 26 is increased, the pressure applied to the valve body 42 is increased and the valve body 42 bends to continue. The passage 40 opens according to the hydraulic pressure to generate a damping force. Then, due to the damping force of the notch 43, the damping force of the valve body 42, or the damping force of the notch 43 and the valve body 42, a restraining force having a magnitude corresponding to the opening speed of the door 26 is generated.
6 to prevent the door 26 from opening suddenly.

Further, when the door 26 is rotated in the closing direction from the state shown in FIG. 12, the shaft 18, and thus the defining member 14, is rotated by its rotating power, and when the door 26 is rotated by a predetermined angle, the door 26 is rotated. Is closed and the defining member 14 is in the state shown in FIG. Due to this rotation, in the defining member 14, the top portion 37a of the defining member-side inclined surface 37 has the cap side inclined surface 3
3 and the inclined surface 32 on the cap side, and linearly moved toward the second chamber 13 (downward in FIG. 1) by the rotational force of the door 26 and the spring force of the spring member 17 at a speed according to the closing speed of the door 26. To do. When the partitioning member 14 moves toward the second chamber 13, the oil liquid flows from the second chamber 13 into the first chamber 12 through the notch 43 and the communication passage 40.

At this time, while the closing speed of the door 26 is low,
The oil passes through the notch 43 without receiving resistance, while the door 2
When the closing speed of 6 increases, the flow of the oil liquid is throttled by the notch 43, and a damping force is generated. Then, due to the damping force of the notch 43, a restraining force having a magnitude corresponding to the closing speed of the door 26 acts on the door 26 to prevent the door 26 from closing abruptly. Here, the apex portion 37a is the inclined surface 32 and the inclined surface 3
3 is guided to the spring member 1
It rotates in the closing direction by the spring force of 7. On the other hand, when the top portion 37a is guided to the flat surface, the spring force of the spring member 17 does not act in the direction of closing the door 26, so that the open state of the door 26 is maintained.

Next, a hinge damper 1 according to a second embodiment of the present invention will be described with reference to FIGS. 14 and 15. The hinge damper 1 of the second embodiment is different from the hinge damper 1 of FIGS. 1 to 13 in that a motion converting mechanism 39A of a different type is provided in place of the motion converting mechanism 39, and other members. , Parts are equivalent, and illustration and description of these equivalent members and parts are omitted as appropriate.

In FIG. 14, an inclined cylinder portion 29A which is concentric with the cylinder member 2 is formed on the side of the defining member 14 of the cap body 28. As shown in FIG. 15, the facing surface of the inclined tubular portion 29A facing the defining member 14 side is an inclined surface that is inclined at a predetermined angle in the direction orthogonal to the tubular member 2. On the second cap 8 side of the defining member body 34, a contact member 35 having a ring shape in plan view is formed. The facing surface of the contact member 35 facing the second cap 8 side is an inclined surface inclined at a predetermined angle in a direction orthogonal to the tubular member 2, and in a predetermined state, the facing surface of the inclined tubular portion 29. It fits and abuts over the entire circumference.

In this hinge damper 1, as in the first embodiment, the defining member 14 and thus the door 2 are opened according to the opening / closing speed.
Suppress opening and closing of 6. Further, the door 26 was opened (Fig. 1
2) after that, when the turning force (the force in the opening direction) of the door 26 is released, the contact member 35 of the defining member 14 is guided by the spring force of the spring member 17 while being guided to the end surface of the inclined tubular portion 29A. The door 26 is pushed down to the side of the second chamber 13 and the door 26 is automatically closed, that is, the automatic return function is exhibited.

Next, a hinge damper 1 according to a third embodiment of the present invention will be described with reference to FIGS. 16 and 17. In the hinge damper 1 of the third embodiment, as compared with the hinge damper 1 (FIGS. 1 to 13) of the first embodiment, the female screw 50 is formed on one end side of the tubular member 2, and the washer 11 is screwed onto the female screw 50. The difference is that they are configured to match.
In this case, the washer 11 is formed with a groove 51 as shown in FIG. 17, and the tubular member 2 is formed by a jig (not shown).
It is possible to adjust the insertion amount of the first cap 7, and thus the insertion amount of the first cap 7. Other members and parts are the same as those of the hinge damper 1 shown in FIGS. 1 to 13, and illustration and description of these equivalent members and parts will be omitted as appropriate.

In this hinge damper 1, by adjusting the screwing amount of the washer 11 to the female screw 50, the insertion amount of the first cap 7 is changed and the basic length of the spring member 17 can be changed. Therefore, the spring force of the spring member 17 is adjusted, and the speed of the linear movement of the defining member 14 and, consequently, the magnitude of the damping force are changed, whereby the opening / closing speed of the door 26 can be adjusted. Further, the opening / closing speed of the door 26 can be kept constant by appropriately adjusting the spring force regardless of the weight of the door 26.

Hinge damper 1 of the fourth embodiment of the present invention
Will be described with reference to FIG. Compared to the hinge damper 1 (FIGS. 1 to 13) of the first embodiment, the hinge damper 1 of the fourth embodiment projects only one end of the shaft 18 outside the tubular member 2 and the other end of the shaft 18. A shaft communication passage 52 for communicating the first and second chambers 12, 13 is formed on the side, and a hole for inserting the shaft 18 of the defining member 14 is formed instead of forming the notch 43 in the valve body 42. A hole 54a is formed inside the defining member 14 instead of providing the notch 53 on the side of the second chamber 13 connected to the second chamber 23 and supporting the one end side of the spring 45 by the second cap 8. The spacer 54 that has been
It is different in that it is configured to support one end side of the. Other members and parts are the same as those of the hinge damper 1 shown in FIGS. 1 to 13, and illustration and description of these equivalent members and parts will be omitted as appropriate.

In this hinge damper 1, only one end of the shaft 18 is projected to the outside of the tubular member 2, and the mounting on the door side bracket 27 can be performed only on one end of the shaft 18, so that the mounting can be simplified. You can In the hinge damper 1 of the first embodiment, the notch 43 is formed in one of the plurality of valve bodies 42 constituting the damping force generating mechanism, but in the present embodiment, the structure of all the valve bodies 42 is the same. Thus, the valve body 42 can be easily manufactured. Also, the spring 4
Since one end side of 5 is supported by the spacer 54 fixed to the defining member 14, the spring force acting on the valve body 42 can be maintained constant regardless of the displacement of the defining member 14. This makes it possible to obtain good damping force characteristics.

[0034]

According to the invention described in claim 1, when the defining member rotates, the defining member is actuated by the operation of the motion converting mechanism.
Linearly moves toward the first chamber or the second chamber, and the oil liquid flows through the damping force generating mechanism due to the differential pressure between the first and second chambers,
When the differential pressure of the oil liquid between the first and second chambers exceeds a predetermined pressure,
Since the damping force generating oil passage generates a damping force to suppress the linear movement of the defining member and thus the rotational speed, the rotational speed of the opened / closed member such as the door held by the defining member via the shaft is controlled. Accordingly, the rotation speed can be suppressed.

According to the second aspect of the present invention, when the defining member is rotated in one direction and then the rotational force in the same direction is released, one of the first and second inclined surfaces has a top portion. First, second
It is possible to rotate the partition member in the other direction by the spring force of the spring member while being guided to the other of the inclined surfaces, and return to the original position.

According to the third aspect of the present invention, when the defining member is rotated in one direction and then the turning force in the same direction is released, one of the first and second inclined surfaces has a top portion. First, second
Of the inclined surface, the partition member is rotated in the other direction by the spring force of the spring member, and the top portion is located on the flat surface formed on the other of the first and second inclined surfaces. Then, the spring force of the spring member does not contribute to the rotation in the other direction, and the rotating position of the defining member, and thus the open / closed state of the opened / closed member, can be maintained.

According to the invention described in claim 4, the insertion depth of the lid portion on the first chamber side can be adjusted with respect to the tubular member, and the basic length of the spring member can be changed. Therefore, the spring force of the spring member is adjusted, the speed of the linear movement of the defining member, and thus the magnitude of the damping force is changed, which makes it possible to adjust the opening / closing speed of the opened / closed member. Further, the opening / closing speed of the opened / closed member can be kept constant by appropriately adjusting the spring force regardless of the weight of the opened / closed member.

[Brief description of the drawings]

FIG. 1 is a cross-sectional view showing a hinge damper according to a first embodiment of the present invention.

FIG. 2 is a plan view showing a defining member and a shaft of the hinge damper.

3 is a cross-sectional view taken along the line AA of FIG.

FIG. 4 is a perspective view schematically showing a defining member of the hinge damper.

FIG. 5 is a bottom view of a tubular member of the hinge damper.

FIG. 6 is a plan view showing a shaft of the hinge damper.

FIG. 7 is a bottom view showing a shaft of the hinge damper.

FIG. 8 is a bottom view showing a second cap of the hinge damper.

FIG. 9 is a bottom view showing a retaining ring of the hinge damper.

FIG. 10 is a bottom view showing a retaining ring of the hinge damper.

FIG. 11 is a sectional view showing a damping force generating mechanism of the hinge damper.

FIG. 12 is a cross-sectional view for explaining the operation of the hinge damper.

FIG. 13 is a plan view showing an example of attachment of the hinge damper.

FIG. 14 is a sectional view showing a hinge damper according to a second embodiment of the present invention.

FIG. 15 is a perspective view schematically showing a second cap of the hinge damper.

FIG. 16 is a sectional view showing a hinge damper according to a third embodiment of the present invention.

FIG. 17 is a plan view showing a screw member of the hinge damper.

FIG. 18 is a sectional view showing a hinge damper according to a fourth embodiment of the present invention.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Hinge damper 2 Cylinder member 7,8 1st, 2nd cap 12,13 1st, 2nd chamber 14 Definition member 17 Spring member 18 Shaft 29 Sloping cylinder part 31 Cap side flat surface 32,33 Cap side inclined surface 35 Contact member 36 Flat member side flat surface 37, 38 Slope surface defining member 39 Motion conversion mechanism 40 Communication passage 42 Valve body 43 Notch

Claims (4)

[Claims] 1. A tubular member having a lid on both ends and having an oil liquid sealed therein, and a shaft provided in the tubular member and extending to the outside from at least one lid of the tubular member, First and second chambers are housed in the tubular member, rotatably engaged with the shaft integrally with the shaft, and axially movable with respect to the shaft. A damping force that communicates the first and second chambers with the partitioning member that defines the first and second chambers and that generates a damping force when the differential pressure of the oil liquid between the first and second chambers exceeds a predetermined pressure. Generating mechanism, the defining member, and the first
A spring member which is interposed between the chamber-side lid portion and the chamber-side lid portion to press the defining member toward the second chamber-side lid portion side, the second chamber-side lid portion, and the defining member. And a motion conversion mechanism that converts the rotation of the defining member into a motion in the axial direction. 2. The motion converting mechanism defines a first inclined surface formed on an opposing surface of the defining member facing the second chamber side lid portion side and a second chamber side lid portion. The hinge damper according to claim 1, wherein the hinge damper is formed on the facing surface facing the member side, and is composed of a second inclined surface that matches the first inclined surface. 3. The motion conversion mechanism defines a first inclined surface formed on an opposing surface of the defining member facing the lid portion side on the second chamber side and a lid portion on the second chamber side. A second inclined surface formed on the opposing surface facing the member side and coinciding with the first inclined surface, and the first inclined surface and the second inclined surface, respectively, so as to coincide with each other in the middle in the circumferential direction. The hinge damper according to claim 1, wherein the hinge damper is formed of a flat surface having a predetermined length in a circumferential direction. 4. The hinge damper according to claim 1, wherein an insertion depth of the lid portion on the first chamber side is adjustable with respect to the tubular member.