CN111042680A

CN111042680A - Hinge with damper

Info

Publication number: CN111042680A
Application number: CN201910387274.3A
Authority: CN
Inventors: 林勝彦; 岩下浩之
Original assignee: Nidec Sankyo Corp
Current assignee: Nidec Instruments Corp
Priority date: 2018-10-15
Filing date: 2019-05-10
Publication date: 2020-04-21
Also published as: JP2020063556A; CN210239418U; CN212743701U

Abstract

A hinge with a damper, which is provided with a fluid damper for damping the rotational movement of a second hinge member with respect to a first hinge member, can simplify the structure of the second hinge member compared to the conventional one. A hinge (1) with a damper is provided with: the damper device is provided with a rotation center shaft (7) which is the rotation center of the second hinge member (6) relative to the first hinge member (5), a swing shaft (10) which rotates together with the second hinge member, a second swing shaft (11) which is arranged in parallel with the rotation center shaft and the swing shaft, is mounted on the second hinge member, and rotates together with the second hinge member, a spring member (12) for applying force to the swing shaft, a fluid damper (13) for damping the rotation action of the second hinge member, a first rod (15) for transmitting the applying force of the spring member to the swing shaft, and a second rod (16) for transmitting the rotation action of the second hinge member to the fluid damper, wherein one end of the second rod is connected with the second swing shaft.

Description

Hinge with damper

Technical Field

The present invention relates to a damper hinge provided with a fluid damper.

Background

Conventionally, a hinge with a damper for a refrigerator is known (for example, see patent document 1). The hinge described in patent document 1 includes an upper frame and a lower frame that are rotatably connected to each other. The upper frame is rotatable about a rotation axis with respect to the lower frame. The lower frame is fixed on the body of the refrigerator, and the upper frame is fixed on the cover of the refrigerator. The hinge described in patent document 1 includes a swing shaft disposed parallel to the rotation shaft and attached to the upper frame, and a compression coil spring for biasing the swing shaft in one direction of the rotation direction of the upper frame.

In the hinge described in patent document 1, a direct-acting fluid damper for relaxing the rotational motion of the upper frame is fixed to a side surface of the lower frame. The hinge described in patent document 1 includes a lever and a connecting member fixed to one end of the lever as a structure for transmitting a rotational motion of an upper frame to a fluid damper. The other end side of the rod is engaged with the fluid damper. The upper frame is formed with a connecting portion that engages with the connecting member.

Documents of the prior art

Patent document

Patent document 1: chinese utility model bulletin No. 206829882 specification

Disclosure of Invention

Technical problem to be solved by the invention

In the hinge described in patent document 1, a connecting portion that engages with the connecting member is formed in the upper frame in order to transmit the pivoting motion of the upper frame to the lever. Therefore, in this hinge, the shape of the upper frame for alleviating the turning operation by the fluid damper becomes complicated. In addition, when the shape of the upper frame becomes complicated, it may be difficult to mount the upper frame on a cover of a refrigerator to which the upper frame is mounted.

Accordingly, an object of the present invention is to provide a hinge with a damper, which includes a first hinge member and a second hinge member rotatably connected to each other, and a fluid damper for damping a rotational movement of the second hinge member with respect to the first hinge member, and which can simplify a structure of the second hinge member as compared with the conventional art.

Technical scheme for solving technical problem

In order to solve the above-described problems, the present invention provides a hinge with a damper, comprising: a first hinge member and a second hinge member rotatably connected; a rotation center shaft that is a rotation center of the second hinge member with respect to the first hinge member; a swing shaft that is arranged in parallel with the rotation center axis and rotates together with the second hinge member with respect to the first hinge member; a second swing shaft that is disposed in parallel with the rotation central shaft and the swing shaft, that is attached to the second hinge member, and that rotates together with the second hinge member with respect to the first hinge member; a spring member for urging the swing shaft toward one side of the second hinge member with respect to the rotational direction of the first hinge member; a fluid damper for moderating a rotational action of the second hinge member with respect to the first hinge member; a first lever for transmitting an urging force of the spring member to the swing shaft; and a second rod for transmitting a rotational motion of the second hinge part with respect to the first hinge part to the fluid damper, an end portion of the second rod being connected to the second swing shaft.

The hinge with damper of the invention comprises: and a second swing shaft attached to the second hinge member and rotating together with the second hinge member with respect to the first hinge member, and a second rod for transmitting a rotating motion of the second hinge member with respect to the first hinge member to the fluid damper, wherein one end of the second rod is connected to the second swing shaft. Therefore, in the present invention, if, for example, an insertion hole through which the second swing shaft is inserted is formed in the second hinge member, the rotational movement of the second hinge member can be transmitted to the second lever via the second swing shaft. Therefore, in the present invention, the structure of the second hinge member can be simplified as compared with the related art. In addition, in the present invention, the rotational movement of the second hinge member with respect to the first hinge member can be transmitted to the second lever with a relatively simple configuration.

In the present invention, for example, one end portion of the second lever is rotatably connected to the second swing shaft.

In the present invention, it is preferable that both end portions of the second swing shaft are supported by the second hinge member. With this configuration, the second swing shaft can be prevented from bending with respect to the second hinge member. Therefore, the rotational movement of the second hinge member with respect to the first hinge member can be reliably transmitted to the second lever.

In the present invention, it is preferable that a restriction groove into which an end portion of the second swing shaft is inserted is formed in the first hinge member, and a rotation range of the second hinge member with respect to the first hinge member is restricted by the end portion of the second swing shaft inserted into the restriction groove and the restriction groove. That is, it is desirable that the rotation range of the second hinge member with respect to the first hinge member is limited by the second swing shaft. When constituted in this way, the structure of the hinge with damper can be simplified.

In the present invention, it is preferable that the second hinge member is connected to the first hinge member at one end side of the first hinge member in the orthogonal direction, and the regulation groove is formed in an arc shape bulging to one side in the second orthogonal direction, when a direction orthogonal to the axial direction of the rotation center shaft is taken as the orthogonal direction and a direction orthogonal to the axial direction and the orthogonal direction of the rotation center shaft is taken as the second orthogonal direction. In this case, it is more desirable that the rotatable angle of the second hinge member with respect to the first hinge member is 90 ° or less.

With this configuration, the amount of movement of the second swing shaft in the orthogonal direction when the second hinge member is rotated relative to the first hinge member can be increased as compared with the case where the restricting groove is formed in an arc shape bulging to one side in the orthogonal direction. Therefore, as compared with the case where the restricting groove is formed in an arc shape bulging toward one side in the orthogonal direction, the amount of movement of the second lever in the orthogonal direction can be increased, and as a result, the amount of movement of the fluid damper when the second hinge member rotates relative to the first hinge member can be increased. Therefore, even if a small and inexpensive fluid damper having a low damping effect is used, the damping force required to appropriately reduce the rotational movement of the second hinge member with respect to the first hinge member can be obtained by the fluid damper. That is, the rotational movement of the second hinge member with respect to the first hinge member can be appropriately relaxed, and a small and inexpensive fluid damper can be used.

In the present invention, it is preferable that the first hinge member includes two flat plate-shaped side surface portions supporting both end portions of the rotation center shaft and a flat plate-shaped base portion connecting the two side surface portions, and the second rod is disposed between the two side surface portions. With this configuration, the hinge with damper can be made smaller in the axial direction of the rotation center shaft than in the case where the second rod is disposed outside both side surface portions in the axial direction of the rotation center shaft.

In the present invention, it is preferable that the damper-equipped hinge includes a link that amplifies the operation amount of the second lever and transmits the amplified operation amount to the fluid damper. With this configuration, the amount of operation of the fluid damper when the second hinge member rotates relative to the first hinge member can be increased. Therefore, even if a small and inexpensive fluid damper having a low damping effect is used, the damping force required to appropriately reduce the rotational movement of the second hinge member with respect to the first hinge member can be obtained by the fluid damper. That is, the rotational movement of the second hinge member with respect to the first hinge member can be appropriately relaxed, and a small and inexpensive fluid damper can be used.

In the present invention, it is preferable that the spring member is a compression coil spring, and when a direction orthogonal to the axial direction of the rotation center shaft is an orthogonal direction, one of the orthogonal directions is a first direction, and an opposite direction of the first direction is a second direction, the second hinge member is connected to the first hinge member on the first direction end side of the first hinge member, the compression coil spring is disposed on the second direction side of the rotation center shaft, the swing shaft, and the second swing shaft, and the fluid damper is disposed on the second direction side of the compression coil spring. With this configuration, the thickness of the damper-equipped hinge in the thickness direction, which is orthogonal to the axial direction and the orthogonal direction of the rotation center axis, can be made thinner than in the case where the fluid damper is disposed on the inner peripheral side of the compression coil spring. That is, the hinge with damper can be made thin.

In the present invention, it is preferable that the hinge with damper includes a brake member that contacts the first lever with a predetermined contact pressure, and a support member that supports the brake member, the spring member is a compression coil spring, the second hinge member is connected to the first hinge member on a first direction end side of the first hinge member when a direction orthogonal to an axial direction of the rotation center shaft is an orthogonal direction, one of the orthogonal directions is a first direction, and an opposite direction of the first direction is a second direction, the compression coil spring is disposed on a second direction side from the rotation center shaft, the swing shaft, and the second swing shaft, the brake member includes a supported portion supported by the support member and a contact portion disposed along the first lever and connected to the supported portion, and is disposed on the second direction side of the compression coil spring, and the supported portion is supported from the second direction side by the supported portion, and is urged from the first direction side by the compression coil spring, and the contact portion is brought into contact with the first lever by the urging force of the compression coil spring.

When so configured, the first lever can be stopped at a predetermined position using the braking member. Further, by stopping the first lever at the predetermined position, the swing shaft that rotates together with the second hinge member with respect to the first hinge member can be stopped at the predetermined position. That is, the second hinge member can be stopped at a predetermined position with respect to the first hinge member. In the above configuration, the contact portion of the brake member is in contact with the first lever by the biasing force of the compression coil spring, so that the first lever can be stopped at the predetermined position by using the compression coil spring for biasing the swing shaft. Therefore, the structure of the hinge with the damper can be simplified as compared with a case where a spring member for bringing the contact portion into contact with the first lever is provided in addition to the compression coil spring. In addition, in the case of such a configuration, since the contact portion is in contact with the first lever by the biasing force of the compression coil spring for biasing the swing shaft, the contact pressure of the contact portion with respect to the first lever can be increased.

(effect of the invention)

As described above, in the damper-equipped hinge according to the present invention, which includes the first hinge member and the second hinge member rotatably coupled to each other, and the fluid damper for damping the rotational movement of the second hinge member with respect to the first hinge member, the structure of the second hinge member can be simplified as compared with the conventional art.

Drawings

Fig. 1 is a perspective view of a damper-equipped hinge according to an embodiment of the present invention.

Fig. 2 is a perspective view of the band damper hinge shown in fig. 1 from a different direction.

Fig. 3 is a front view of the damper-equipped hinge shown in fig. 1.

Fig. 4 is a side view for explaining a state in which the damper hinge shown in fig. 1 is mounted on the locker.

Fig. 5 is an enlarged view of a portion E of fig. 4.

FIG. 6 is an enlarged view of the E-section of FIG. 4 showing the cabinet with the cover opened.

Fig. 7 is a perspective view of a state where the first hinge part is detached from the band damper hinge shown in fig. 1.

Fig. 8 is a side view for explaining operations of the second hinge member, the swing shaft, the second swing shaft, and the like shown in fig. 7.

Fig. 9 is a diagram for explaining the structure of the first lever and the like shown in fig. 1.

Fig. 10 is a diagram for explaining the structure and operation of the brake member shown in fig. 1.

Description of the reference numerals

1: hinge assembly

5: first hinge part

5 a: side surface part

5 b: base part

5 d: limiting groove

6: second hinge part

7: rotating central shaft

10: oscillating shaft

11: second swing shaft

12: compression coil spring

13: fluid damper

15: first rod

16: second rod

17: connecting rod

18: brake component

18 a: supported part

18 b: contact part

19: support member

X: axial direction of the rotating central shaft

Y: second orthogonal direction

Z: orthogonal direction

Z1: a first direction

Z2: second direction

Detailed Description

Embodiments of the present invention will be described below with reference to the drawings.

(outline structure of hinge with damper)

Fig. 1 is a perspective view of a damper-equipped hinge 1 according to an embodiment of the present invention. Fig. 2 is a perspective view showing the band damper hinge 1 shown in fig. 1 from a different direction. Fig. 3 is a front view of the damper hinge 1 shown in fig. 1. Fig. 4 is a side view for explaining a state where the damper hinge 1 shown in fig. 1 is mounted on the locker 2. Fig. 5 is an enlarged view of a portion E of fig. 4. FIG. 6 is an enlarged view of the section E of FIG. 4 showing the opened state of the cover 4 of the cabinet 2.

The damper-equipped hinge 1 (hereinafter referred to as "hinge 1") according to the present embodiment is an instrument for attaching a cover 4 to a main body 3 of a storage cabinet 2 such as a refrigerator or an ice chest and enabling opening and closing (see fig. 4 to 6). The hinge 1 includes a first hinge member 5 and a second hinge member 6 which are rotatably connected to each other, and a rotation center shaft 7 which serves as a rotation center of the second hinge member 6 with respect to the first hinge member 5. The first hinge member 5 is fixed to the body 3 and the second hinge member 6 is fixed to the cover 4.

The second hinge member 6 is rotatable with respect to the first hinge member 5 between an open position 6A (position shown in fig. 6) in which the cover 4 is open and a closed position 6B (position shown in fig. 4 and 5) in which the cover 4 is closed. The second hinge member 6 is rotatable at an angle (rotatable range) of 90 ° or less with respect to the first hinge member 5. In the present embodiment, the rotatable angle of the second hinge member 6 with respect to the first hinge member 5 is about 75 °.

In the following description, an axial direction (X direction in fig. 3 and the like) of the rotation center shaft 7 is referred to as a "left-right direction", a Y direction in fig. 3 and the like orthogonal to the left-right direction is referred to as a "front-rear direction", and a Z direction in fig. 3 and the like orthogonal to the left-right direction and the front-rear direction is referred to as a "up-down direction". Further, one of the left and right directions, that is, the X1 direction in fig. 3 and the like is referred to as the "right" direction, the opposite direction, that is, the X2 direction in fig. 3 and the like is referred to as the "left" direction, one of the front and rear directions, that is, the Y1 direction in fig. 5 and the like is referred to as the "front" direction, the opposite direction, that is, the Y2 direction in fig. 5 and the like is referred to as the "rear" direction, one of the up and down directions, that is, the Z1 direction in fig. 3 and the like is referred to as the "up" direction, and the opposite direction, that is, the Z2.

The vertical direction (Z direction) in the present embodiment is an orthogonal direction orthogonal to the horizontal direction, which is the axial direction of the rotation center shaft 7. In the present embodiment, the upward direction (Z1 direction) is a first direction that is one of the orthogonal directions, and the downward direction (Z2 direction) is a second direction that is the opposite direction of the first direction. In the present embodiment, the front-rear direction (Y direction) is a second orthogonal direction orthogonal to the left-right direction as the axial direction of the rotation center shaft 7 and the up-down direction as the orthogonal direction. In the present embodiment, the storage cabinet 2 is provided so that the vertical direction (Z direction) and the up-down direction coincide with each other. The storage cabinet 2 is provided with a cover 4 disposed on the upper side of the main body 3. When the user who uses the storage cabinet 2 opens the closed lid 4, the lid 4 is lifted by rotating around the rotation center shaft 7.

Further, the hinge 1 includes: a swing shaft 10 that is arranged in parallel with the rotation center shaft 7 and rotates together with the second hinge member 6 with respect to the first hinge member 5; a second swing shaft 11 that is arranged parallel to the rotation central shaft 7 and the swing shaft 10 and rotates together with the second hinge member 6 with respect to the first hinge member 5; a spring member 12 for urging the swing shaft 10 to one side in the rotational direction of the second hinge member 6 with respect to the first hinge member 5; and a fluid damper 13 for moderating a rotational action of the second hinge member 6 with respect to the first hinge member 5. The spring member 12 of the present embodiment is a compression coil spring. Therefore, hereinafter, the spring member 12 is referred to as a "compression coil spring 12".

The hinge 1 further includes a first lever 15 for transmitting the biasing force of the compression coil spring 12 to the swing shaft 10, a second lever 16 for transmitting the rotational motion of the second hinge member 6 with respect to the first hinge member 5 to the fluid damper 13, and a link 17 for amplifying the rotational motion of the second hinge member 6 with respect to the first hinge member 5 and transmitting the amplified rotational motion to the fluid damper 13. The hinge 1 further includes a stopper member 18 that comes into contact with the first lever 15 at a predetermined contact pressure. The hinge 1 of the present embodiment includes a plurality of braking members 18. Specifically, the hinge 1 includes two braking members 18. The hinge 1 further includes a support member 19 that supports the brake member 18, and a damper holding member 20 that holds the fluid damper 13 (see fig. 3). Note that, in fig. 1 and 2, the damper holding member 20 is not shown.

(concrete Structure of hinge with damper)

Fig. 7 is a perspective view of the hinge 1 shown in fig. 1 in a state where the first hinge member 5 is detached.

Fig. 8 is a side view for explaining operations of the second hinge member 6, the swing shaft 10, the second swing shaft 11, and the like shown in fig. 7. Fig. 9 is a diagram for explaining the structure of the first lever 15 and the like shown in fig. 1. Fig. 10 is a diagram for explaining the structure and operation of the braking member 18 shown in fig. 1.

The first hinge member 5 is formed by bending a metal plate such as a steel plate into a predetermined shape. The first hinge member 5 includes two flat plate-shaped side surface portions 5a that support both end portions of the rotation center shaft 7, and a flat plate-shaped base portion 5b that connects the two side surface portions 5 a. The side surface portion 5a is disposed so that the thickness direction of the side surface portion 5a coincides with the left-right direction, and the base portion 5b is disposed so that the thickness direction of the base portion 5b coincides with the front-rear direction.

The two side surface parts 5a are erected from both ends of the base part 5b in the left-right direction toward the front side, respectively. The first hinge member 5 is formed in a substantially square groove shape as a whole. The upper end of the side surface portion 5a is a protrusion 5c protruding upward from the upper end of the base portion 5 b. On the body 3 of the storage cabinet 2, the base 5b is fixed by screws or the like so that the rear surface of the base 5b is in contact with the body 3.

The second hinge member 6 is formed by bending a metal plate such as a steel plate into a predetermined shape. The second hinge member 6 includes two flat plate-shaped side surface portions 6a and a flat plate-shaped base portion 6b connecting the two side surface portions 6a, as in the first hinge member 5. The side surface portion 6a is disposed so that the thickness direction of the side surface portion 6a coincides with the left-right direction. That is, the side surface portion 6a is arranged parallel to the side surface portion 5 a.

When the second hinge member 6 is disposed at the closed position 6B, the base portion 6B is disposed such that the thickness direction of the base portion 6B coincides with the front-rear direction, and the two side surface portions 6a rise from both end portions of the base portion 6B in the left-right direction toward the front side. The second hinge member 6 is formed in a substantially square groove shape as a whole. The base portion 6B is fixed to the cover 4 of the cabinet 2 by screws or the like so that the rear surface of the base portion 6B is in contact with the cover 4 when the second hinge member 6 is disposed at the closed position 6B.

The width of the first hinge member 5 in the left-right direction is wider than the width of the second hinge member 6 in the left-right direction. The two side surface portions 6a are disposed inside the two protruding portions 5c in the left-right direction, and are sandwiched by the two protruding portions 5 c. That is, the two side surface portions 6a are arranged between the two side surface portions 5a in the left-right direction. The side surface portion 6a is formed with insertion holes through which both end portions of the rotation center shaft 7 are inserted, respectively. The insertion hole is a circular hole penetrating the side surface portion 6a in the left-right direction.

The rotation center shaft 7 is formed in a cylindrical shape. Both end portions of the rotation center shaft 7 are fixed to the side surface portion 5 a. Specifically, both end portions of the rotation center shaft 7 are fixed to the upper end portions of the two projecting portions 5c, respectively, and the second hinge member 6 is connected to the first hinge member 5 on the upper end side of the first hinge member 5. In addition, the second hinge member 6 is connected to the first hinge member 5 at the front end side of the first hinge member 5. When the second hinge member 6 is rotated about the rotation center shaft 7 so that the upper end portion of the second hinge member 6 in the closed position 6B moves to the front side, the second hinge member 6 in the closed position 6B moves to the open position 6A.

The swing shaft 10 is formed in a cylindrical shape. Both ends of the swing shaft 10 are supported by the second hinge member 6. Specifically, both end portions of the swing shaft 10 are fixed to the two side surface portions 6a, respectively. As shown in fig. 8 (a), when the second hinge member 6 is at the closed position 6B, the swing shaft 10 is disposed below the rotation center shaft 7. Specifically, when the second hinge member 6 is at the closed position 6B, the swing shaft 10 is disposed slightly forward from just below the rotation center shaft 7. As shown in fig. 8 (B), when the second hinge member 6 is at the open position 6A, the swing shaft 10 is disposed obliquely rearward and downward of the rotation center shaft 7.

When the second hinge member 6 rotates relative to the first hinge member 5, the swing shaft 10 moves in the vertical direction. The amount of vertical movement of the swing shaft 10 when the second hinge member 6 is rotated at a certain angle with respect to the first hinge member 5 decreases as the swing shaft 10 moves directly below the rotation center shaft 7.

The right end of the swing shaft 10 is disposed on the left side of the left surface of the protrusion 5c so as not to contact the protrusion 5c disposed on the right side, and the left end of the swing shaft 10 is disposed on the right side of the right surface of the protrusion 5c so as not to contact the protrusion 5c disposed on the left side. The swing shaft 10 is inserted through a brake member 23 formed in a cylindrical shape. The brake member 23 is disposed between the two side surface portions 6 a. A recess 23a that is recessed inward in the radial direction of the braking member 23 is formed at the center position of the braking member 23 in the left-right direction. The recess 23a is formed over the entire circumferential area of the brake member 23.

The second swing shaft 11 is formed in a cylindrical shape. Both ends of the second swing shaft 11 are supported by the second hinge member 6. Specifically, both end portions of the second swing shaft 11 are fixed to the two side surface portions 6a, respectively. That is, the second swing shaft 11 is attached to the second hinge member 6. Both end portions of the second swing shaft 11 protrude outward in the left-right direction from the side surface portion 6 a. An insertion hole through which the second swing shaft 11 is inserted is formed in the side surface portion 6 a. The insertion hole is a circular hole penetrating the side surface portion 6a in the left-right direction.

In both side surface parts 5a of the first hinge member 5, a regulating groove 5d into which an end of the second swing shaft 11 is inserted is formed. That is, the first hinge member 5 is formed with a restriction groove 5 d. The restriction groove 5d is formed in the projection 5 c. The restriction groove 5d penetrates the protrusion 5c in the left-right direction. The restricting groove 5d is formed in an arc shape having the axis of the rotation center shaft 7 as the center of curvature when viewed in the left-right direction. The restricting groove 5d is formed in an arc shape bulging rearward.

The range of rotation of the second hinge member 6 relative to the first hinge member 5 is limited by the end of the second swing shaft 11 inserted into the limiting groove 5d and the limiting groove 5 d. As described above, since the second hinge member 6 can rotate at an angle of 90 ° or less with respect to the first hinge member 5, the central angle of the arcuate regulation groove 5d (the central angle centered on the axial center of the rotation center shaft 7) is 90 ° or less. In the present embodiment, the central angle of the regulating groove 5d is about 75 °.

As shown in fig. 8, when the second hinge member 6 is at the closed position 6B, the second swing shaft 11 is disposed obliquely rearward and below the rotation center shaft 7, and when the second hinge member 6 is at the open position 6A, the second swing shaft 11 is disposed obliquely rearward and above the rotation center shaft 7. When the second hinge member 6 rotates with respect to the first hinge member 5, the second swing shaft 11 moves in the up-down direction. The amount of movement of the second swing shaft 11 in the vertical direction when the second hinge member 6 is rotated at a certain angle with respect to the first hinge member 5 is almost constant regardless of the rotational position of the second hinge member 6. Further, when the second hinge member 6 is rotated by a certain angle with respect to the first hinge member 5, the amount of movement of the second swing shaft 11 in the vertical direction is larger than the amount of movement of the swing shaft 10 in the vertical direction.

The first rod 15 is formed in a substantially rectangular flat plate shape elongated in the vertical direction. The first lever 15 is disposed so that the thickness direction of the first lever 15 coincides with the left-right direction. The first lever 15 is constituted by an upper lever portion 15a constituting an upper portion of the first lever 15 and a lower lever portion 15b constituting a lower portion of the first lever 15. The upper rod portion 15a has a width in the front-rear direction larger than that of the lower rod portion 15 b. A step surface is formed at the boundary between the upper rod part 15a and the lower rod part 15 b. A concave curved surface is formed at the upper end of the first lever 15, and the concave curved surface is formed in an arc shape. The concave curved surface is in contact with the outer peripheral surface of the braking member 23. Specifically, the concave curved surface contacts the bottom surface of the concave portion 23a of the brake member 23.

As shown in fig. 9, the first rod 15 is inserted through the

washers

24, 25 and the

guide members

26, 27. The washer 24 is formed in a disk shape, and the washer 25 is formed in a rectangular flat plate shape. The

washers

24 and 25 are arranged such that the thickness direction and the vertical direction of the

washers

24 and 25 substantially coincide with each other. The guide member 26 is formed in a flanged cylindrical shape having a flange portion 26a and a column portion 26b, and the guide member 27 is formed in a cylindrical shape. The

guide members

26, 27 are arranged so that the axial direction and the vertical direction of the

guide members

26, 27 substantially coincide with each other. The washer 24, the guide member 26, the guide member 27, and the washer 25 are arranged in this order from the upper side toward the lower side.

The

washers

24 and 25 and the

guide members

26 and 27 are formed with insertion holes through which the lower rod portions 15b are inserted, and the lower rod portions 15b are inserted. The upper surface of the washer 24 is in surface contact with a step formed at the boundary between the upper rod portion 15a and the lower rod portion 15 b. The washer 24 is restricted from moving upward relative to the first rod 15 by the upper surface of the washer 24 contacting the step surface. That is, the downward movement of the first rod 15 with respect to the washer 24 is restricted. The upper surface of the flange portion 26a of the guide member 26 contacts the lower surface of the washer 24.

The outer diameter of the flange 26a formed in a disc shape is larger than the outer diameter of the compression coil spring 12. The upper end of the compression coil spring 12 contacts the lower surface of the flange portion 26 a. The column portion 26b of the guide member 26 is inserted through the upper end portion of the compression coil spring 12. The washer 25 formed in a rectangular plate shape has a shorter side longer than the outer diameter of the compression coil spring 12. The gasket 25 is disposed so that the longitudinal direction of the gasket 25 coincides with the lateral direction. The lower end of the compression coil spring 12 is in contact with the upper surface of the washer 25. The guide member 27 is inserted through the lower end portion of the compression coil spring 12. The lower end surface of the guide member 27 is in contact with the upper surface of the washer 25. The

guide members

26, 27 function to prevent the compression coil spring 12 from being displaced in the radial direction.

As shown in fig. 10, the brake member 18 includes a supported portion 18a supported by the support member 19 and a contact portion 18b arranged along the first lever 15. The braking member 18 of the present embodiment is composed of a supported portion 18a and a contact portion 18 b. The braking member 18 is formed by bending a metal plate such as a steel plate into a substantially L shape, and the supported portion 18a and the contact portion 18b are formed in a flat plate shape. The contact portion 18b is connected to one end of the supported portion 18 a. An angle θ (see fig. 10 a) formed by the supported portion 18a and the contact portion 18b is an obtuse angle. In the present embodiment, the angle θ is 95 ° to 100 °.

The two brake members 18 are disposed so as to sandwich the first lever 15 in the left-right direction. That is, the two braking members 18 are disposed so as to sandwich the first rod 15 formed in a flat plate shape in the thickness direction of the first rod 15. Specifically, the two contact portions 18b are disposed so as to sandwich the lower rod portion 15b in the left-right direction. The contact portion 18b is disposed so that the thickness direction of the contact portion 18b substantially coincides with the left-right direction. In the brake member 18 disposed on the right side, the supported portion 18a extends rightward from the upper end of the contact portion 18 b. In the brake member 18 disposed on the left side, the supported portion 18a extends from the upper end of the contact portion 18b toward the left side.

The braking member 18 is disposed below the compression coil spring 12. The supported portion 18a is disposed below the washer 25 and above the support member 19. That is, the supported portion 18a is disposed between the supporting member 19 and the washer 25 in the vertical direction. The supported portion 18a is supported from below by the support member 19. The supported portion 18a is biased from above by the compression coil spring 12. Specifically, the supported portion 18a is biased from above by the compression coil spring 12 via the washer 25.

The support member 19 is formed by bending a metal plate such as a steel plate into a predetermined shape. Both ends of the support member 19 in the left-right direction are supported from below by support portions 5e formed on the side surface portions 5 a. The support portion 5e is formed in a flat plate shape. The support portion 5e stands upright from the two side surface portions 5a toward the inside in the left-right direction. The support portion 5e is disposed so that the thickness direction of the support portion 5e coincides with the front-rear direction. The support member 19 supports the two brake members 18 from the lower side. The support member 19 supports the compression coil spring 12 from below via the brake member 18 and the washer 25.

As shown in fig. 10, the support member 19 is formed with a through hole 19a through which the two contact portions 18b and the lower rod portion 15b are inserted. The through hole 19a penetrates the support member 19 in the vertical direction. The through hole 19a is formed in a rectangular shape. As shown in fig. 10, on the upper surface of the support member 19, the boundary between the supported portion 18a and the contact portion 18b contacts the edge of the through hole 19a in the left-right direction.

The compression coil spring 12 is disposed below the rotation center shaft 7, the swing shaft 10, and the second swing shaft 11. As described above, the lower end of the compression coil spring 12 is in contact with the upper surface of the washer 25. The compression coil spring 12 is supported from below by the supporting portion 5e of the first hinge member 5 via the washer 25, the supported portion 18a, and the supporting member 19. As described above, the upper end of the compression coil spring 12 contacts the lower surface of the flange portion 26a of the guide member 26. The compression coil spring 12 biases the first rod 15 upward with respect to the first hinge member 5 via the flange portion 26a and the washer 24.

The upper end of the first lever 15 is in contact with the stopper member 23 at a prescribed contact pressure. The first lever 15 biases the swing shaft 10 via the brake member 23 toward one side in the rotation direction of the second hinge member 6 about the rotation center axis 7 by the biasing force of the compression coil spring 12. That is, the compression coil spring 12 biases the swing shaft 10 fixed to the second hinge member 6 toward one side in the rotation direction of the second hinge member 6 about the rotation center axis 7. That is, the compression coil spring 12 biases the second hinge member 6 to one side in the rotational direction of the second hinge member 6 about the rotational center axis 7.

Specifically, the compression coil spring 12 biases the swing shaft 10 in a direction in which the second hinge member 6 moves from the closed position 6B to the open position 6A. In the present embodiment, when the second hinge member 6 is at the closed position 6B, the swing shaft 10 is disposed slightly forward of the position immediately below the rotation center axis 7, and therefore, strictly speaking, when the swing shaft 10 is at the position immediately forward of the position immediately below the rotation center axis 7, the compression coil spring 12 biases the second hinge member 6 in the direction in which the second hinge member 6 is toward the closed position 6B.

As described above, when the second hinge member 6 rotates relative to the first hinge member 5, the swing shaft 10 moves in the up-down direction, and therefore, the first lever 15 also moves in the up-down direction. Therefore, when the second hinge member 6 rotates relative to the first hinge member 5, the biasing force of the compression coil spring 12 biasing the swing shaft 10 varies. The biasing force of the compression coil spring 12 biasing the swing shaft 10 becomes maximum when the swing shaft 10 is disposed directly below the rotation center shaft 7.

As described above, the supported portion 18a of the brake member 18 is supported from below by the support member 19 and is biased from above by the compression coil spring 12. The two contact portions 18b are disposed so as to sandwich the lower rod portion 15b in the left-right direction, and a boundary portion between the supported portion 18a and the contact portion 18b contacts an edge of the through hole 19a in the left-right direction on the upper surface of the supporting member 19. In the present embodiment, the brake member 18 is rotated about the boundary between the supported portion 18a and the contact portion 18B as a fulcrum by the biasing force of the compression coil spring 12, and the contact portion 18B is brought into contact with the lower lever portion 15B of the first lever 15 (see fig. 10B).

The contact pressure of the contact portion 18b with respect to the lower rod portion 15b of the first rod 15 varies according to the urging force of the compression coil spring 12. Specifically, when the first lever 15 is lowered and the urging force of the compression coil spring 12 is increased, the contact pressure of the contact portion 18b with respect to the lower lever portion 15b becomes high. Further, when the contact portion 18B is in contact with the lower lever portion 15B, since a braking force acts on the first lever 15, the braking force acts on the second hinge member 6 that rotates toward the closed position 6B. In the present embodiment, as described above, the upper end of the first lever 15 is in contact with the brake member 23 at a predetermined contact pressure, and therefore, the braking force is also applied to the second hinge member 6 by the action of the brake member 23.

In the present embodiment, in a range in which the resultant force of the braking force of the second hinge member 6 by the action of the

braking members

18 and 23 and the urging force of the second hinge member 6 by the compression coil spring 12 is larger than the gravity acting on the cover 4, even if the user who performs the opening and closing operation of the cover 4 of the storage cabinet 2 separates his hand from the cover 4, the second hinge member 6 stops relative to the first hinge member 5. That is, even if the user who performs the opening and closing operation of the storage cabinet 2 separates his hand from the lid 4, the lid 4 is stopped. For example, in a range in which the second hinge member 6 is rotated by 30 ° from the open position 6A toward the closed position 6B, even if the user who performs the opening and closing operation of the lid 4 separates his hand from the lid 4, the lid 4 is stopped.

Further, in the present embodiment, since the amount of movement in the vertical direction of the swing shaft 10 immediately after the second hinge member 6 starts rotating from the open position 6A toward the closed position 6B is large, the amount of movement in the vertical direction of the first lever 15 immediately after the second hinge member 6 starts rotating from the open position 6A toward the closed position 6B is large. Therefore, since the second hinge member 6 starts to rotate from the open position 6A toward the closed position 6B, the biasing force of the compression coil spring 12 can be made to act on the supported portion 18a of the brake member 18 relatively largely immediately, and as a result, the braking force of the second hinge member 6 by the action of the brake member 18 is easily generated immediately after the second hinge member 6 starts to rotate from the open position 6A toward the closed position 6B.

The second rod 16 is formed in a substantially rectangular flat plate shape elongated in the vertical direction. The second lever 16 is disposed so that the thickness direction of the second lever 16 coincides with the left-right direction. The second rod 16 is disposed between the two side surface portions 5 a. The second rod 16 is disposed along one side surface portion 5a of the two side surface portions 5 a. Specifically, the second lever 16 is disposed along the side surface portion 5a disposed on the right side.

The second rod 16 is disposed between one side surface portion 5a of the two side surface portions 5a and one side surface portion 6a of the two side surface portions 6a in the left-right direction. Specifically, the second lever 16 is disposed between the side surface portion 5a disposed on the right side and the side surface portion 6a disposed on the right side in the left-right direction. The second lever 16 is disposed on the right side of the right end of the swing shaft 10. The front end of the second rod 16 is arranged rearward of the front end of the side surface portion 5 a.

The upper end (one end) of the second lever 16 is connected to the second swing shaft 11. Specifically, the upper end of the second lever 16 is rotatably connected to the second swing shaft 11. As shown in fig. 8, an insertion hole 16a through which the right end of the second swing shaft 11 is inserted is formed in the upper end portion of the second lever 16. The insertion hole 16a is a circular hole that penetrates the second rod 16 in the left-right direction. The second lever 16 is formed with a slit hole 16b in the shape of a slit whose longitudinal direction is the vertical direction. The slit hole 16b is a square hole that penetrates the second lever 16 in the left-right direction.

The support portion 5e formed on the side surface portion 5a disposed on the right side is inserted into the slit hole 16 b. The slit hole 16b has a width in the front-rear direction larger than the thickness of the support portion 5 e. In the present embodiment, the support portion 5e formed on the right side surface portion 5a is a guide portion for guiding the second rod 16 in the vertical direction. The support portion 5e supports the lower end of the compression coil spring 12 via the washer 25, the supported portion 18a, and the support member 19.

The fluid damper 13 is a direct-acting fluid damper. The fluid damper 13 is an oil damper, and a fluid chamber filled with oil (viscous oil) is formed inside a housing of the fluid damper 13. The fluid damper 13 is disposed such that a piston rod of the fluid damper 13 protrudes downward. The housing and the piston rod of the fluid damper 13 are formed of resin. The fluid damper 13 is disposed below the compression coil spring 12. The fluid damper 13 is disposed between the two side surface portions 5 a.

The fluid damper 13 is disposed on the left side of the center of the first hinge member 5 in the left-right direction. The fluid damper 13 is disposed on the front side of the base portion 5 b. The front end of the fluid damper 13 is disposed rearward of the front end of the side surface portion 5 a. As described above, the fluid damper 13 is held by the damper holding member 20. The damper holding member 20 is formed of resin. The damper holding member 20 is formed in a substantially rectangular parallelepiped block shape.

The damper retaining member 20 is fixed to the first hinge member 5. Specifically, the damper holding member 20 is fixed to the lower end portion of the first hinge member 5. The damper holding member 20 is disposed between the two side surface portions 5 a. The damper holding member 20 is disposed on the front side of the base portion 5 b. The front surface of the damper holding member 20 is disposed slightly rearward of the front end of the side surface portion 5 a.

The link 17 is formed in a flat plate shape. The links 17 are arranged such that the thickness direction of the links 17 coincides with the front-rear direction. The link 17 is a pivotal lever that is pivotable about a pivotal center axis 30. The rotation center shaft 30 is formed in a cylindrical shape. The rotation center shaft 30 is disposed so that the axial direction of the rotation center shaft 30 coincides with the front-rear direction. That is, the link 17 can rotate in the axial direction in which the forward and backward directions are rotational. The rotation center shaft 30 is fixed to the link 17. The rotation center shaft 30 is held by the damper holding member 20 and is rotatable. That is, the link 17 is rotatably held by the damper holding member 20.

The link 17 amplifies the amount of motion of the second lever 16 and transmits it to the fluid damper 13. That is, the link 17 accelerates the movement of the second lever 16 and transmits the same to the fluid damper 13. The lower end of the second lever 16 is engaged with the right end of the link 17 from above. A recess portion that engages with the right end portion of the link 17 is formed in the lower end portion of the second lever 16 so as to be recessed upward from the lower end of the second lever 16. The piston rod of the fluid damper 13 is in contact with the left end of the connecting rod 17 from the upper side.

As shown in fig. 3, when the point of action of the link 17 on which the force from the fluid damper 13 acts is the first point of action 17a, and the point of action of the link 17 on which the force from the second lever 16 (i.e., the force from the second hinge member 6) acts is the second point of action 17b, the distance L1 between the first point of action 17a and the axial center of the rotation center shaft 30 is greater than the distance L2 between the second point of action 17b and the axial center of the rotation center shaft 30. Specifically, the distance L1 is 2 times or more the distance L2. In the present embodiment, the distance L1 is about 2 times the distance L2.

In the present embodiment, when the second hinge member 6 rotates from the open position 6A toward the closed position 6B, the second rod 16 descends, the link 17 rotates, and the piston rod of the fluid damper 13 is pushed up. Further, the rotational operation of the second hinge member 6 that rotates toward the closed position 6B is alleviated by raising the piston rod of the fluid damper 13. That is, when the cover 4 is closed, the rotational movement of the second hinge member 6 with respect to the first hinge member 5 is alleviated.

(main effect of the present embodiment)

As described above, in the present embodiment, the hinge 1 includes the second swing shaft 11 attached to the second hinge member 6 and rotating together with the second hinge member 6, and the second lever 16 for transmitting the rotating motion of the second hinge member 6 with respect to the first hinge member 5 to the fluid damper 13, and the upper end portion of the second lever 16 is rotatably connected to the second swing shaft 11. Therefore, in the present embodiment, if the second hinge member 6 is formed with an insertion hole through which the second swing shaft 11 is inserted, the rotation operation of the second hinge member 6 can be transmitted to the second lever 16 via the second swing shaft 11. Therefore, in the present embodiment, the structure of the second hinge member 6 can be simplified. In addition, in the present embodiment, the rotational movement of the second hinge member 6 with respect to the first hinge member 5 can be transmitted to the second lever 16 with a relatively simple configuration.

In the present embodiment, both end portions of the second swing shaft 11 are supported by the second hinge member 6. Therefore, in the present embodiment, the bending of the second swing shaft 11 with respect to the second hinge member 6 can be suppressed. Therefore, in the present embodiment, the rotational movement of the second hinge member 6 with respect to the first hinge member 5 can be reliably transmitted to the second lever 16.

In the present embodiment, the rotation range of the second hinge member 6 with respect to the first hinge member 5 is restricted by the restriction groove 5d formed on the first hinge member 5 and the end portion of the second swing shaft 11 inserted into the restriction groove 5 d. That is, in the present embodiment, the second swing shaft 11 is used to restrict the range of rotation of the second hinge member 6 with respect to the first hinge member 5. Therefore, in the present embodiment, the structure of the hinge 1 can be simplified.

In the present embodiment, the restriction groove 5d is formed in an arc shape bulging rearward. In the present embodiment, the rotatable angle of the second hinge member 6 with respect to the first hinge member 5 is 90 ° or less. Therefore, in the present embodiment, the amount of movement of the second pivot shaft 11 in the vertical direction when the second hinge member 6 pivots relative to the first hinge member 5 can be increased as compared to the case where the restriction groove 5d is formed in an arc shape bulging downward. Therefore, in the present embodiment, as compared with the case where the restricting groove 5d is formed in an arc shape bulging downward, the operation amount of the second rod 16 in the vertical direction can be increased, and as a result, the operation amount of the fluid damper 13 when the second hinge member 6 rotates with respect to the first hinge member 5 can be increased.

Therefore, in the present embodiment, even if the fluid damper 13 having a low damping effect, which is relatively small and inexpensive, is used, the damping force required for appropriately damping the rotational movement of the second hinge member 6 with respect to the first hinge member 5 can be obtained by the fluid damper 13. That is, in the present embodiment, the rotational movement of the second hinge member 6 with respect to the first hinge member 5 can be appropriately relaxed, and the fluid damper 13 which is small and inexpensive can be used.

In addition, in the present embodiment, since the hinge 1 includes the link 17 that amplifies the operation amount of the second lever 16 and transmits the amplified operation amount to the fluid damper 13, the operation amount of the fluid damper 13 when the second hinge member 6 rotates with respect to the first hinge member 5 can be increased. Therefore, in the present embodiment, even if the fluid damper 13 having a lower damping effect and being small and inexpensive is used, the damping force required for appropriately damping the rotational operation of the second hinge member 6 with respect to the first hinge member 5 can be obtained by the fluid damper 13. That is, in the present embodiment, the rotational movement of the second hinge member 6 with respect to the first hinge member 5 can be appropriately relaxed, and a smaller and less expensive fluid damper 13 can be used.

In the present embodiment, the second rod 16 is disposed between the two side surface portions 5 a. Therefore, in the present embodiment, the hinge 1 can be made smaller in the lateral direction as compared with the case where the second lever 16 is disposed outside the two side surface portions 5a in the lateral direction. In addition, in the present embodiment, since the fluid damper 13 is disposed below the compression coil spring 12, the thickness of the hinge 1 in the front-rear direction can be made thinner as compared with the case where the fluid damper 13 is disposed on the inner peripheral side of the compression coil spring 12. That is, in the present embodiment, the hinge 1 can be thinned.

In the present embodiment, the hinge 1 includes the stopper member 18 that comes into contact with the first lever 15 at a predetermined contact pressure. Therefore, in the present embodiment, the first lever 15 can be stopped at the predetermined position using the brake member 18, and as a result, the second hinge member 6 can be stopped at the predetermined position with respect to the first hinge member 5 as described above.

In the present embodiment, since the contact portion 18b of the brake member 18 is in contact with the first lever 15 by the biasing force of the compression coil spring 12, the first lever 15 can be stopped at a predetermined position using the compression coil spring 12 for biasing the swing shaft 10. Therefore, in the present embodiment, the structure of the hinge 1 can be simplified as compared with a case where a spring member for bringing the contact portion 18b into contact with the first lever 15 is provided in addition to the compression coil spring 12. In the present embodiment, the contact portion 18b is in contact with the first lever 15 by the biasing force of the compression coil spring 12 for biasing the swing shaft 10, and therefore the contact pressure of the contact portion 18b with respect to the first lever 15 can be increased.

(other embodiments)

The above embodiment is an example of the best mode of the present invention, but is not limited thereto, and various modifications can be made without departing from the scope of the present invention.

In the above-described embodiment, the fluid damper 13 may be arranged such that the piston rod of the fluid damper 13 protrudes upward. In this case, the lower end surface of the housing of the fluid damper 13 is in contact with the left end portion of the link 17 from the upper side. In the above-described embodiment, the fluid damper 13 may be a rotary fluid damper. In the above-described embodiment, the fluid chamber of the fluid damper 13 may be filled with a viscous fluid other than oil. For example, the fluid damper 13 may be a gas damper in which the fluid chamber is filled with air.

In the above-described embodiment, the whole or a part of the fluid damper 13 may protrude outward in the lateral direction of the two side surface parts 5 a. In the above-described embodiment, the fluid damper 13 may be disposed so as to be parallel to the compression coil spring 12 in the left-right direction, or may be disposed on the inner peripheral side of the compression coil spring 12. In the above embodiment, the second rod 16 may be disposed on the right side of the side surface portion 5a disposed on the right side, or may be disposed on the left side of the side surface portion 6a disposed on the right side.

In the above-described embodiment, the first operating point 17a is disposed on the left side of the rotation center shaft 30, and the second operating point 17b is disposed on the right side of the rotation center shaft 30, but the first operating point 17a and the second operating point 17b may be disposed on the left side of the rotation center shaft 30. In this case, for example, the rotation center shaft 30 is disposed on the right side of the side surface portion 5a disposed on the right side. In this case, for example, the fluid damper 13 is disposed such that the piston rod of the fluid damper 13 protrudes upward, and the left end of the link 17 contacts the piston rod of the fluid damper 13 from above.

In the above embodiment, the link 17 may be rotatable in the axial direction in which the left-right direction is rotatable. In this case, for example, the entire or a part of the fluid damper 13 is disposed at a position forward of the front end of the side surface portion 5 a. In the above-described embodiment, the distance L1 between the first operating point 17a and the axis of the rotation center shaft 30 may be greater than the distance L2 between the second operating point 17b and the axis of the rotation center shaft 30 and less than 2 times the distance L2. The distance L1 and the distance L2 may be equal.

In the above embodiment, the hinge 1 may not include the link 17. That is, the motion of the second rod 16 may be directly transmitted to the fluid damper 13. In this case, for example, the fluid damper 13 is disposed such that the piston rod of the fluid damper 13 protrudes upward, and the lower end of the second rod 16 contacts the piston rod of the fluid damper 13 from above.

In the above-described embodiment, the swing shaft 10 may be used to limit the range of rotation of the second hinge member 6 with respect to the first hinge member 5. In the above-described embodiment, the pivoting range of the second hinge part 6 in one side of the pivoting direction of the second hinge member 6 with respect to the first hinge member 5 may be restricted by the pivoting shaft 10, and the pivoting range of the second hinge part 6 in the other side of the pivoting direction of the second hinge member 6 may be restricted by the second pivoting shaft 11.

In the above-described embodiment, the rotatable angle of the second hinge member 6 relative to the first hinge member 5 may also be greater than 90 °. In the above embodiment, the swing shaft 10 may be formed integrally with the second hinge member 6. In the above embodiment, the brake member 23 may be formed integrally with the first lever 15. In this case, the braking force of the second hinge member 6 due to the action of the braking member 23 is not generated. In the above-described embodiment, the hinge 1 may not include the braking member 18, and may not include the braking member 23.

Claims

1. A hinge with a damper is characterized by comprising:

a first hinge member and a second hinge member rotatably connected;

a rotation center shaft that is a rotation center of the second hinge member with respect to the first hinge member;

a swing shaft that is arranged in parallel with the rotation center shaft and rotates together with the second hinge member with respect to the first hinge member;

a second swing shaft that is disposed in parallel with the rotation center shaft and the swing shaft, that is attached to the second hinge member, and that rotates together with the second hinge member with respect to the first hinge member;

a spring member for urging the swing shaft to one side of a rotational direction of the second hinge member with respect to the first hinge member;

a fluid damper for moderating a rotational action of the second hinge member relative to the first hinge member;

a first lever for transmitting the urging force of the spring member to the swing shaft; and

a second rod for transmitting rotational motion of the second hinge member relative to the first hinge member to the fluid damper,

one end of the second rod is connected with the second swinging shaft.

2. The damper hinge of claim 1,

one end portion of the second lever is rotatably connected to the second swing shaft.

3. The damper hinge according to claim 1 or 2,

both end portions of the second swing shaft are supported by the second hinge member.

4. The damper hinge according to any one of claims 1 to 3,

a restricting groove into which an end portion of the second swing shaft is inserted is formed on the first hinge member,

the rotation range of the second hinge member with respect to the first hinge member is restricted by the end of the second swing shaft inserted into the restriction groove and the restriction groove.

5. The damper hinge of claim 4,

when a direction orthogonal to the axial direction of the rotation center axis is defined as an orthogonal direction, and a direction orthogonal to the axial direction of the rotation center axis and the orthogonal direction is defined as a second orthogonal direction,

the second hinge member is connected to the first hinge member at one end side of the first hinge member in the orthogonal direction,

the restriction groove is formed in an arc shape bulging to one side in the second orthogonal direction.

6. The damper hinge of claim 5,

the second hinge member is rotatable at an angle of 90 ° or less with respect to the first hinge member.

7. The damper hinge according to any one of claims 1 to 6,

the first hinge member includes: two flat-plate-shaped side surface portions supporting both end portions of the rotation center shaft; and a flat plate-like base portion connecting the two side surface portions,

the second rod is disposed between the two side surface portions.

8. The damper hinge according to any one of claims 1 to 7,

the damper includes a link rod that amplifies the amount of motion of the second lever and transmits the amplified amount of motion to the fluid damper.

9. The damper hinge according to any one of claims 1 to 8,

the spring member is a compression coil spring,

when a direction orthogonal to the axial direction of the rotation center shaft is set as an orthogonal direction, one of the orthogonal directions is set as a first direction, and a direction opposite to the first direction is set as a second direction,

the second hinge member is connected to the first hinge member at a first-direction end side of the first hinge member,

the compression coil spring is disposed on a second direction side with respect to the rotation center shaft, the swing shaft, and the second swing shaft,

the fluid damper is disposed on a second direction side of the compression coil spring.

10. The damper hinge according to any one of claims 1 to 9,

the disclosed device is provided with: a brake member that contacts the first lever at a predetermined contact pressure; and a support member supporting the braking member,

the spring member is a compression coil spring,

the brake member includes: a supported portion supported by the support member; and a contact portion arranged along the first rod and connected to the supported portion, and the braking member is arranged on a second direction side of the compression coil spring,

the supported portion is supported from the second direction side by the supporting member and is biased from the first direction side by the compression coil spring,

the contact portion is in contact with the first lever by the urging force of the compression coil spring.