JP2020063557A - Hinge with damper - Google Patents

Abstract

To provide a hinge with damper including a fluid damper for relaxing the turning operation of a second hinge member with respect to a first hinge member, capable of developing cushioning force required to properly relaxing the turning operation of the second hinge member using the relatively small and inexpensive fluid damper having a low cushioning effect.SOLUTION: A hinge with damper 1 includes a turning center shaft 7 serving as the turning center of a second hinge member 6 with respect to a first hinge member 5, an oscillation shaft 10 arranged in parallel to the turning center shaft 7 for turning together with the second hinge member 6, a spring member 12 for energizing the oscillation shaft 10 to one side in the turning direction of the second hinge member 6 with respect to the first hinge member 5, a fluid damper 13 for relaxing the turning operation of the second hinge member 6 with respect to the first hinge member 5, and a link lever 17 for amplifying the turning quantity of the second hinge member 6 with respect to the first hinge member 5 and transmitting it to the fluid damper 13.SELECTED DRAWING: Figure 2

Description

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

  Conventionally, a hinge with a damper used in a refrigerator is known (for example, refer to Patent Document 1). The hinge described in Patent Document 1 includes a mounting bracket that is fixed to the body of the refrigerator and a rotating arm that is fixed to the lid of the refrigerator. The rotating arm is rotatable with respect to the mounting bracket about a rotation center axis. Further, the hinge described in Patent Document 1 is arranged in parallel with the rotation center axis and is attached to the rotation arm, and biases the rotation axis in one of the rotation directions of the rotation arm (specifically, Specifically, a compression coil spring for biasing the swing shaft in the direction in which the lid opens) is provided. A direct-acting fluid damper is arranged on the inner peripheral side of the compression coil spring to mitigate the rotational movement of the rotary arm. The motion of the rotary arm is directly transmitted to the piston rod of the fluid damper via the push-pull shaft and the swing shaft.

China utility model publication No. 206737651

  In the hinge described in Patent Document 1, since the motion of the rotating arm is directly transmitted to the piston rod of the fluid damper, unless a large and expensive fluid damper having a high cushioning effect is used, the rotating arm with respect to the mounting bracket is It becomes difficult for the fluid damper to obtain the cushioning force required to appropriately alleviate the rotational movement. Therefore, in the hinge described in Patent Document 1, the size of the hinge increases and the cost of the hinge increases.

  Then, the subject of this invention is a damper provided with the 1st hinge member and the 2nd hinge member which are connected so that rotation is possible, and the fluid damper for mitigating the rotation operation of the 2nd hinge member with respect to a 1st hinge member. In the attached hinge, even if a relatively small and inexpensive fluid damper having a low cushioning effect is used, the fluid damper provides a cushioning force necessary to appropriately mitigate the rotational movement of the second hinge member with respect to the first hinge member. It is to provide a hinge with a damper that can be obtained.

  In order to solve the above-mentioned problems, a hinge with a damper of the present invention includes a first hinge member and a second hinge member that are rotatably connected to each other, and a rotation center of the second hinge member with respect to the first hinge member. A moving center axis, a swinging axis arranged parallel to the rotating center axis and rotating together with the second hinge member relative to the first hinge member, and rotation of the second hinge member relative to the first hinge member. A spring member for urging the swing shaft toward one side in the direction, a fluid damper for alleviating the rotational movement of the second hinge member with respect to the first hinge member, and a second hinge member for the first hinge member. And a link lever for amplifying the amount of rotation and transmitting the amplified amount to the fluid damper.

  The damper hinge of the present invention includes a link lever for amplifying the rotation amount of the second hinge member with respect to the first hinge member and transmitting the amplified amount to the fluid damper. Therefore, in the present invention, it is possible to increase the operation amount of the fluid damper when the second hinge member rotates with respect to the first hinge member. Therefore, according to the present invention, even if a relatively small and inexpensive fluid damper having a low cushioning effect is used, the cushioning force required to appropriately alleviate the rotational movement of the second hinge member with respect to the first hinge member is used. You can get it with a damper. That is, according to the present invention, it is possible to use a relatively small-sized and inexpensive fluid damper while appropriately mitigating the rotational movement of the second hinge member with respect to the first hinge member.

  In the present invention, for example, the link lever is a turning lever that is turnable about the second turning center axis, and the action point where the force from the fluid damper acts on the link lever is the first action point. Assuming that the action point of the link lever on which the force from the second hinge member acts is the second action point, the distance between the first action point and the axis of the second rotation center axis is the second action point and the second action point. It is longer than the distance from the axis of the two-rotation center axis. In this case, for example, the distance between the first action point and the axis of the second rotation center shaft is twice or more the distance between the second action point and the axis of the second rotation center shaft. There is.

  In the present invention, if the direction orthogonal to the axial direction of the rotation center axis is the orthogonal direction and the direction orthogonal to the axial direction of the rotation center axis is the second orthogonal direction, the second hinge member is orthogonal. It is preferable that one end side of the first hinge member in the direction is connected to the first hinge member, and the link lever is rotatable about the second orthogonal direction as the rotation axis direction. According to this structure, the size of the hinge with damper can be reduced in the second orthogonal direction as compared with the case where the link lever is rotatable about the axial direction of the central axis of rotation. Will be possible. That is, it is possible to reduce the thickness of the hinge with damper.

  In the present invention, the hinge with damper includes a first lever for transmitting the urging force of the spring member to the swing shaft and a first lever for transmitting the rotational movement of the second hinge member with respect to the first hinge member to the fluid damper. It is preferable that the link lever includes two levers, and the link lever amplifies the operation amount of the second lever and transmits it to the fluid damper. When the rotational movement of the second hinge member with respect to the first hinge member is transmitted to the fluid damper via the first lever and the link lever, the second hinge member is rotated with respect to the first hinge member at each rotational position of the second hinge member. It is difficult to freely set the biasing force of the spring member acting on the hinge member and the buffer force of the fluid damper acting on the second hinge member. However, with this configuration, the first lever and the second lever are used. , Setting the biasing force of the spring member acting on the second hinge member and the buffering force of the fluid damper acting on the second hinge member relatively freely at each rotational position of the second hinge member with respect to the first hinge member. Will be possible.

  In the present invention, the hinge with damper includes a second swing shaft that is arranged in parallel with the rotation center axis and the swing axis and that rotates together with the second hinge member with respect to the first hinge member. It is preferable that one end of the two levers is rotatably connected to the second swing shaft. According to this structure, the rotation operation of the second hinge member with respect to the first hinge member can be transmitted to the second lever with a relatively simple structure.

  In the present invention, for example, the fluid damper is a direct-acting fluid damper. Further, in the present invention, the hinge with damper includes, for example, a resin damper holding member that holds the fluid damper and is fixed to the first hinge member. In this case, it is preferable that the link lever is rotatably held by the damper holding member. According to this structure, it is not necessary to separately provide a member for holding the link lever in addition to the damper holding member. Therefore, it is possible to simplify the configuration of the hinge with damper.

  In the present invention, the spring member is a compression coil spring, and the direction orthogonal to the axial direction of the rotation center axis is the orthogonal direction, one of the orthogonal directions is the first direction, and the opposite direction of the first direction is the second direction. Then, the second hinge member is connected to the first hinge member at the first direction end side of the first hinge member, and the compression coil spring is arranged on the second direction side with respect to the rotation center axis and the swing axis. The damper is preferably arranged on the second direction side with respect to the compression coil spring. With this configuration, the thickness in the thickness direction of the hinge with a damper orthogonal to the axial direction of the rotation center axis is orthogonal to that in the case where the fluid damper is arranged on the inner peripheral side of the compression coil spring. Can be made thinner. That is, it is possible to reduce the thickness of the hinge with damper.

  In the present invention, the damper-equipped hinge includes a first lever for transmitting the biasing force of the spring member to the swing shaft, a brake member that comes into contact with the first lever at a predetermined contact pressure, and a support member that supports the brake member. The spring member is a compression coil spring, and the direction orthogonal to the axial direction of the rotation center axis is the orthogonal direction, one of the orthogonal directions is the first direction, and the opposite direction of the first direction is the second direction. Then, the second hinge member is connected to the first hinge member on the first direction end side of the first hinge member, and the compression coil spring is arranged on the second direction side with respect to the rotation center axis and the swing shaft, and the brake is applied. The member includes a supported portion supported by the supporting member, a contact portion arranged along the first lever and connected to the supported portion, and the member is disposed on the second direction side of the compression coil spring. Supported by the support member from the second direction side Is biased to the compression coil spring from the first direction with the contact portion is preferably in contact with the first lever by the urging force of the compression coil spring.

  According to this structure, the first lever can be stopped at the predetermined position by using the brake member. Further, by stopping the first lever at a predetermined position, it becomes possible to stop the swing shaft that rotates together with the second hinge member with respect to the first hinge member at the predetermined position. That is, the second hinge member can be stopped at a predetermined position with respect to the first hinge member. Further, according to this structure, the contact portion of the brake member comes into contact with the first lever by the urging force of the compression coil spring, so that the compression coil spring for urging the swing shaft is used to move the first lever to a predetermined position. Can be stopped with. Therefore, the configuration of the hinge with damper can be simplified as compared with the 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. Further, according to this structure, the contact portion comes into contact with the first lever by the urging force of the compression coil spring for urging the swing shaft, so that the contact pressure of the contact portion with respect to the first lever can be increased. Become.

  As described above, in the present invention, the first hinge member and the second hinge member that are rotatably connected to each other, and the fluid damper for relaxing the rotation operation of the second hinge member with respect to the first hinge member are provided. In the hinge with a damper, even if a relatively small and inexpensive fluid damper having a low cushioning effect is used, the cushioning force necessary to appropriately alleviate the rotational movement of the second hinge member relative to the first hinge member is provided. Can be obtained at.

It is a perspective view of a hinge with a damper concerning an embodiment of the invention. It is a perspective view which shows the hinge with a damper shown in FIG. 1 from a different direction. It is a front view of the hinge with a damper shown in FIG. It is a side view for demonstrating the state where the hinge with a damper shown in FIG. 1 was attached to the storage. It is an enlarged view of the E section of FIG. FIG. 5 is an enlarged view of a portion E of FIG. 4 in a state where a lid of the storage case is opened. It is a perspective view of the state where the 1st hinge member was removed from the damper hinge shown in FIG. FIG. 8 is a side view for explaining the movement of the second hinge member, the swing shaft, the second swing shaft, and the like shown in FIG. 7. It is a figure for demonstrating the structure of a 1st lever etc. which are shown in FIG. It is a figure for demonstrating the structure and movement of the brake member shown in FIG.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings.

(Schematic structure of hinge with damper)
FIG. 1 is a perspective view of a hinge 1 with a damper according to an embodiment of the present invention. FIG. 2 is a perspective view showing the damper hinge 1 shown in FIG. 1 from a different direction. FIG. 3 is a front view of the hinge 1 with a damper shown in FIG. FIG. 4 is a side view for explaining a state in which the damper hinge 1 shown in FIG. 1 is attached to the storage case 2. FIG. 5 is an enlarged view of portion E in FIG. FIG. 6 is an enlarged view of a portion E of FIG. 4 in a state where the lid 4 of the storage case 2 is opened.

  The hinge 1 with a damper (hereinafter referred to as “hinge 1”) of the present embodiment is a device for attaching the lid 4 to the main body 3 of the storage 2 such as a refrigerator or a freezer so that the lid 4 can be opened and closed (FIGS. (See FIG. 6). The hinge 1 includes a first hinge member 5 and a second hinge member 6 that are rotatably connected, and a rotation center shaft 7 that is a rotation center of the second hinge member 6 with respect to the first hinge member 5. There is. The first hinge member 5 is fixed to the main body 3, and the second hinge member 6 is fixed to the lid 4.

  The second hinge member 6 includes the first hinge member 5 between the open position 6A (the position shown in FIG. 6) where the lid 4 opens and the closed position 6B (the position shown in FIGS. 4 and 5) where the lid 4 closes. It is rotatable with respect to. The rotatable angle (rotatable range) of the second hinge member 6 with respect to the first hinge member 5 is 90 ° or less. In this 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, the axial direction of the rotation center shaft 7 (X direction in FIG. 3 and the like) is referred to as “left and right direction”, and the Y direction in FIG. The Z direction in FIG. 3 and the like orthogonal to the direction is referred to as the “vertical direction”. Further, the X1 direction in FIG. 3 or the like, which is one of the left and right directions, is the “right” direction, the X2 direction in FIG. 3 or the like, which is the opposite direction, is the “left” direction, and the Y1 in FIG. The direction is the "front" direction, the Y2 direction in FIG. 5 or the like, which is the opposite direction, is the "back" direction, and the Z1 direction in FIG. 3 or the like, which is one of the up and down directions, is the "up" direction, which is the opposite direction. The Z2 direction in FIG. 3 etc. is referred to as the “down” direction.

  The up-down direction (Z direction) of this embodiment is an orthogonal direction orthogonal to the left-right direction which is the axial direction of the rotation center shaft 7. In the present embodiment, the upward direction (Z1 direction) is the first direction that is one of the orthogonal directions, and the downward direction (Z2 direction) is the second direction that is the opposite direction of the first direction. There is. Further, in the present embodiment, the front-rear direction (Y direction) is a second orthogonal direction that is orthogonal to the left-right direction that is the axial direction of the rotation center shaft 7 and the up-down direction that is the orthogonal direction. In the present embodiment, the storage case 2 is installed so that the vertical direction (Z direction) and the vertical direction coincide with each other. Further, the storage case 2 is installed so that the lid 4 is arranged above the main body 3. When opening the closed lid 4, the user who uses the storage 2 pivots the lid 4 around the pivot shaft 7 and lifts it.

  Further, the hinge 1 is disposed in parallel with the rotation center shaft 7, and swings with the second hinge member 6 relative to the first hinge member 5, and the swing center shaft 7 and the swing shaft 10. A second swing shaft 11 that is arranged parallel to the moving shaft 10 and that rotates together with the second hinge member 6 with respect to the first hinge member 5, and a rotation of the second hinge member 6 with respect to the first hinge member 5. A spring member 12 for urging the swing shaft 10 toward one side in the moving direction, and a fluid damper 13 for relaxing the rotational movement of the second hinge member 6 with respect to the first hinge member 5 are provided. The spring member 12 of this embodiment is a compression coil spring. Therefore, in the following, the spring member 12 is referred to as a "compression coil spring 12".

  Further, the hinge 1 transmits to the fluid damper 13 the first lever 15 for transmitting the biasing force of the compression coil spring 12 to the swing shaft 10 and the rotational movement of the second hinge member 6 with respect to the first hinge member 5. And a link lever 17 for amplifying the rotational movement of the second hinge member 6 with respect to the first hinge member 5 and transmitting it to the fluid damper 13. Further, the hinge 1 includes a brake member 18 that comes into contact with the first lever 15 with a predetermined contact pressure. The hinge 1 of the present embodiment includes a plurality of brake members 18. Specifically, the hinge 1 includes two brake members 18. The hinge 1 also includes a support member 19 that supports the brake member 18, and a damper holding member 20 (see FIG. 3) that holds the fluid damper 13. It should be noted that the damper holding member 20 is not shown in FIGS. 1 and 2.

(Specific configuration of hinge with damper)
FIG. 7 is a perspective view of the hinge 1 shown in FIG. 1 with the first hinge member 5 removed. FIG. 8 is a side view for explaining the movement of the second hinge member 6, the swing shaft 10, the second swing shaft 11 and the like shown in FIG. FIG. 9 is a diagram for explaining the configuration of the first lever 15 and the like shown in FIG. FIG. 10 is a diagram for explaining the configuration and movement of the brake member 18 shown in FIG.

  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 is provided with two flat plate-shaped side surface portions 5a that support both ends of the rotation center shaft 7 and a flat plate-shaped base portion 5b that connects the two side surface portions 5a. The side surface portion 5a is arranged so that the thickness direction of the side surface portion 5a and the left-right direction coincide with each other, and the base portion 5b is arranged so that the thickness direction of the base portion 5b coincides with the front-rear direction.

  Each of the two side surface portions 5a rises from the respective end portions of the base portion 5b in the left-right direction toward the front side. 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 protruding portion 5c protruding upward from the upper end of the base portion 5b. The base 5b is fixed to the main body 3 of the storage case 2 with screws or the like so that the rear surface of the base 5b contacts the main body 3.

  The second hinge member 6 is formed by bending a metal plate such as a steel plate into a predetermined shape. Similar to the first hinge member 5, 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. The side surface portion 6a is arranged such that the thickness direction of the side surface portion 6a and the left-right direction coincide with each other. That is, the side surface portion 6a is arranged in parallel with the side surface portion 5a.

  Further, when the second hinge member 6 is arranged at the closed position 6B, the base portion 6b is arranged so that the thickness direction of the base portion 6b and the front-back direction coincide with each other, and the two side surface portions 6a have the same shape. Each rises toward the front side from each of both ends of the base portion 6b in the left-right direction. The second hinge member 6 is formed in a substantially square groove shape as a whole. The base 6b is fixed to the lid 4 of the storage case 2 by a screw or the like so that the rear surface of the base 6b contacts the lid 4 when the second hinge member 6 is arranged at the closed position 6B.

  The lateral width of the first hinge member 5 is wider than the lateral width of the second hinge member 6. The two side surface portions 6a are arranged inside the two protruding portions 5c in the left-right direction, and are sandwiched between the two protruding portions 5c. 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 ends of the rotation center shaft 7 are inserted. This insertion hole is a round hole that penetrates the side surface portion 6a in the left-right direction.

  The rotation center shaft 7 is formed in a cylindrical shape. Both ends of the rotation center shaft 7 are fixed to the side surface portion 5a. Specifically, both ends of the rotation center shaft 7 are fixed to the upper ends of the two projecting portions 5c, respectively, and the second hinge member 6 is located on the upper end side of the first hinge member 5 and has a first position. It is connected to the hinge member 5. The second hinge member 6 is connected to the first hinge member 5 on the front end side of the first hinge member 5. When the second hinge member 6 rotates about the rotation center axis 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. Move to 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 ends of the swing shaft 10 are fixed to each of the two side surfaces 6a. As shown in FIG. 8A, the swing shaft 10 is arranged below the rotation center shaft 7 when the second hinge member 6 is in the closed position 6B. Specifically, when the second hinge member 6 is in the closed position 6B, the swing shaft 10 is arranged slightly forward of the position directly below the rotation center shaft 7. Further, as shown in FIG. 8B, the swing shaft 10 is disposed obliquely behind and below the rotation center shaft 7 when the second hinge member 6 is at the open position 6A.

  The swing shaft 10 moves in the vertical direction when the second hinge member 6 rotates with respect to the first hinge member 5. The vertical movement amount of the swing shaft 10 when the second hinge member 6 is rotated by a certain angle with respect to the first hinge member 5 is as the swing shaft 10 moves directly below the rotation center shaft 7. It is getting smaller.

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

  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 each of the two side surface portions 6a. That is, the second swing shaft 11 is attached to the second hinge member 6. Both ends of the second swing shaft 11 project outward in the left-right direction from the side surface portion 6a. The side surface portion 6a is formed with an insertion hole through which the second swing shaft 11 is inserted. This insertion hole is a round hole that penetrates the side surface portion 6a in the left-right direction.

  A restriction groove 5d into which the end of the second swing shaft 11 is inserted is formed in each of the two side surface portions 5a of the first hinge member 5. That is, the restriction groove 5d is formed in the first hinge member 5. The restriction groove 5d is formed on the protrusion 5c. The restriction groove 5d penetrates the protrusion 5c in the left-right direction. The restriction groove 5d is formed in an arc shape with the center of curvature of the rotation center shaft 7 as the center of curvature when viewed in the left-right direction. The restriction groove 5d is formed in an arc shape that bulges backward.

  The rotation range of the second hinge member 6 with respect to the first hinge member 5 is restricted by the end of the second swing shaft 11 inserted into the restriction groove 5d and the restriction groove 5d. As described above, since the rotatable angle of the second hinge member 6 with respect to the first hinge member 5 is 90 ° or less, the central angle of the restriction groove 5d formed in an arc shape (the rotational center shaft 7 The center angle about the axis of is 90 ° or less. In this embodiment, the central angle of the restriction groove 5d is about 75 °.

  As shown in FIG. 8, when the second hinge member 6 is in the closed position 6B, the second swing shaft 11 is arranged obliquely behind and below the rotation center shaft 7, and the second hinge member 6 is opened. When it is in the position 6A, it is disposed diagonally rearward and upward of the rotation center shaft 7. The second swing shaft 11 moves in the vertical direction when the second hinge member 6 rotates with respect to the first hinge member 5. The amount of vertical movement of the second swing shaft 11 when the second hinge member 6 is rotated by a certain angle with respect to the first hinge member 5 is irrelevant regardless of the rotating position of the second hinge member 6. It does not change. Further, the amount of vertical movement of the second swing shaft 11 when the second hinge member 6 rotates by a certain angle with respect to the first hinge member 5 is greater than the amount of vertical movement of the swing shaft 10. It is getting bigger.

  The first lever 15 is formed in a substantially rectangular flat plate shape elongated in the vertical direction. The first lever 15 is arranged so that the thickness direction of the first lever 15 and the left-right direction coincide with each other. The first lever 15 is composed of an upper lever portion 15a that constitutes an upper portion of the first lever 15 and a lower lever portion 15b that constitutes a lower portion of the first lever 15. The width of the upper lever portion 15a in the front-rear direction is wider than the width of the lower lever portion 15b in the front-rear direction. A step surface is formed at the boundary between the upper lever portion 15a and the lower lever portion 15b. A concave curved surface formed in an arc shape is formed on the upper end of the first lever 15. The concave curved surface is in contact with the outer peripheral surface of the brake member 23. Specifically, the concave curved surface is in contact with the bottom surface of the concave portion 23a of the brake member 23.

  As shown in FIG. 9, the first lever 15 is inserted through the washers 24, 25 and the guide members 26, 27. The washer 24 is formed in a disc shape, and the washer 25 is formed in a rectangular flat plate shape. The washers 24 and 25 are arranged so that the thickness direction of the washers 24 and 25 and the up-down direction substantially match. The guide member 26 is formed in a columnar shape with a collar having a flange portion 26a and a column portion 26b, and the guide member 27 is formed in a columnar shape. The guide members 26 and 27 are arranged so that the axial direction of the guide members 26 and 27 and the up-down direction substantially match. The washer 24, the guide member 26, the guide member 27, and the washer 25 are arranged in this order from the upper side to the lower side.

  The washers 24, 25 and the guide members 26, 27 are formed with insertion holes through which the lower lever portion 15b is inserted, and the lower lever portion 15b is inserted therethrough. The upper surface of the washer 24 is in contact with the step surface formed at the boundary between the upper lever portion 15a and the lower lever portion 15b. By contacting the upper surface of the washer 24 with the stepped surface, upward movement of the washer 24 with respect to the first lever 15 is restricted. That is, the downward movement of the first lever 15 with respect to the washer 24 is restricted. The lower surface of the washer 24 is in contact with the upper surface of the flange portion 26 a of the guide member 26.

  The outer diameter of the flange portion 26 a 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 is in contact with the lower surface of the collar portion 26a. The column portion 26b of the guide member 26 is inserted into the upper end portion of the compression coil spring 12. The length of the short side of the washer 25 formed in the shape of a rectangular flat plate is longer than the outer diameter of the compression coil spring 12. The washer 25 is arranged so that the direction of the long side of the washer 25 and the left-right direction match. The lower end of the compression coil spring 12 is in contact with the upper surface of the washer 25. A guide member 27 is inserted through the lower end 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 and 27 have a function of preventing 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 18 a supported by the support member 19 and a contact portion 18 b arranged along the first lever 15. The brake member 18 of this embodiment includes a supported portion 18a and a contact portion 18b. The brake 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 18a. An angle θ formed by the supported portion 18a and the contact portion 18b (see FIG. 10A) is an obtuse angle. In the present embodiment, the angle θ is 95 ° to 100 °.

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

  The brake member 18 is arranged below the compression coil spring 12. The supported portion 18 a is arranged below the washer 25 and above the support member 19. That is, the supported portion 18 a is arranged between the support member 19 and the washer 25 in the vertical direction. The supported portion 18a is supported by the support member 19 from below. The supported portion 18a is biased by the compression coil spring 12 from above. Specifically, the supported portion 18 a is biased by the compression coil spring 12 from above 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 in the left-right direction of the support member 19 are supported from below by a support portion 5e formed on the side surface portion 5a. The support portion 5e is formed in a flat plate shape. The support portion 5e rises inward in the left-right direction from the two side surface portions 5a. The support portion 5e is arranged such that the thickness direction of the support portion 5e and the front-rear direction coincide with each other. The support member 19 supports the two brake members 18 from the lower side. Further, 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 into which the two contact portions 18b and the lower lever 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 is in contact with the edge of the through hole 19a in the left-right direction.

  The compression coil spring 12 is arranged 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 support portion 5e of the first hinge member 5 via the washer 25, the supported portion 18a, and the support member 19. Further, as described above, the upper end of the compression coil spring 12 is in contact with the lower surface of the flange portion 26 a of the guide member 26. The compression coil spring 12 biases the first lever 15 upward with respect to the first hinge member 5 via the collar portion 26a and the washer 24.

  The upper end of the first lever 15 is in contact with the brake member 23 with a predetermined contact pressure. Further, the first lever 15 moves the swing shaft 10 to one side in the rotation direction of the second hinge member 6 about the rotation center shaft 7 via the brake member 23 by the urging force of the compression coil spring 12. I am biased. 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 shaft 7. That is, the compression coil spring 12 biases the second hinge member 6 toward one side in the rotation direction of the second hinge member 6 about the rotation center shaft 7.

  Specifically, the compression coil spring 12 biases the swing shaft 10 in the 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 in the closed position 6B, the swing shaft 10 is arranged slightly forward of the position directly below the rotation center shaft 7, and thus, strictly speaking, the swing shaft 10 does not swing. When the shaft 10 is located on the front side of the center of rotation 7 directly below, the compression coil spring 12 biases the second hinge member 6 in the direction in which the second hinge member 6 moves toward the closed position 6B.

  As described above, when the second hinge member 6 rotates with respect to the first hinge member 5, the swing shaft 10 moves in the vertical direction, so that the first lever 15 also moves in the vertical direction. Therefore, the biasing force of the compression coil spring 12 that biases the swing shaft 10 changes when the second hinge member 6 rotates with respect to the first hinge member 5. The biasing force of the compression coil spring 12 that biases the swing shaft 10 becomes maximum when the swing shaft 10 is arranged directly below the rotation center shaft 7.

  As described above, the supported portion 18a of the brake member 18 is supported by the support member 19 from below and is biased by the compression coil spring 12 from above. Further, the two contact portions 18b are arranged so as to sandwich the lower lever portion 15b in the left-right direction, and on the upper surface of the support member 19, the supported portion 18a and the contact portion are provided at the edge of the through hole 19a in the left-right direction. The boundary with 18b is in contact. In this embodiment, the urging force of the compression coil spring 12 causes the brake member 18 to rotate about the boundary between the supported portion 18a and the contact portion 18b as a fulcrum, so that the contact portion 18b moves toward 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 lever portion 15b of the first lever 15 varies according to the biasing force of the compression coil spring 12. Specifically, when the first lever 15 descends and the biasing force of the compression coil spring 12 increases, the contact pressure of the contact portion 18b with respect to the lower lever portion 15b increases. When the contact portion 18b comes into contact with the lower lever portion 15b, the braking force acts on the first lever 15, so that 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 with a predetermined contact pressure, so that the brake force also acts on the second hinge member 6 by the action of the brake member 23. To do.

  In the present embodiment, in the range where the total force of the braking force of the second hinge member 6 by the action of the brake 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 lid 4, The second hinge member 6 stops with respect to the first hinge member 5 even when the user who opens and closes the lid 4 of the storage case 2 releases the hand from the lid 4. That is, even if the user who opens and closes the storage case 2 releases the lid 4, the lid 4 is stopped. For example, in the range in which the second hinge member 6 is rotated 30 ° from the open position 6A to the closed position 6B, even if the user who performs the opening / closing operation of the lid 4 releases the lid 4, the lid 4 stops. To do.

  In the present embodiment, the vertical movement amount of the swing shaft 10 immediately after the second hinge member 6 starts rotating from the open position 6A to the closed position 6B is relatively large, and thus the second hinge member 6 is provided. The amount of vertical movement of the first lever 15 is relatively large immediately after starting rotation from the open position 6A to the closed position 6B. Therefore, a relatively large biasing force of the compression coil spring 12 can be applied to the supported portion 18a of the brake member 18 immediately after the second hinge member 6 starts rotating from the open position 6A to the closed position 6B. As a result, the braking force of the second hinge member 6 due to the action of the brake member 18 is easily generated immediately after the second hinge member 6 starts rotating from the open position 6A toward the closed position 6B.

  The second lever 16 is formed in a substantially rectangular flat plate shape elongated in the vertical direction. The second lever 16 is arranged so that the thickness direction of the second lever 16 and the left-right direction coincide with each other. The second lever 16 is arranged between the two side surface portions 5a. In addition, the second lever 16 is arranged along one side surface portion 5a of the two side surface portions 5a. Specifically, the second lever 16 is arranged along the side surface portion 5a arranged on the right side.

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

  The upper end portion (one end portion) of the second lever 16 is connected to the second swing shaft 11. Specifically, the upper end portion of the second lever 16 is rotatably connected to the second swing shaft 11. As shown in FIG. 8, an insertion hole 16 a through which the right end of the second swing shaft 11 is inserted is formed in the upper end of the second lever 16. The insertion hole 16a is a round hole that penetrates the second lever 16 in the left-right direction. The second lever 16 is formed with a slit-shaped slit hole 16b 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 arranged on the right side is inserted into the slit hole 16b. The width of the slit hole 16b in the front-rear direction is wider than the thickness of the support portion 5e. In the present embodiment, the support portion 5e formed on the right side surface portion 5a serves as a guide portion that guides the second lever 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 the case body of the fluid damper 13. The fluid damper 13 is arranged such that the piston rod of the fluid damper 13 projects downward. The case body and the piston rod of the fluid damper 13 are made of resin. The fluid damper 13 is arranged below the compression coil spring 12. Further, the fluid damper 13 is arranged between the two side surface portions 5a.

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

  The damper holding 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 arranged between the two side surface portions 5a. The damper holding member 20 is arranged on the front side of the base portion 5b. The front surface of the damper holding member 20 is arranged slightly behind the front end of the side surface portion 5a.

  The link lever 17 is formed in a flat plate shape. The link lever 17 is arranged so that the thickness direction of the link lever 17 and the front-back direction match. The link lever 17 is a rotation lever that is rotatable around the rotation center shaft 30. The rotation center shaft 30 is formed in a cylindrical shape. The rotation center shaft 30 is arranged such that the axial direction of the rotation center shaft 30 and the front-rear direction coincide with each other. That is, the link lever 17 is rotatable about the front-rear direction as the axis of rotation.

  The rotation center shaft 30 is fixed to the link lever 17. The rotation center shaft 30 is rotatably held by the damper holding member 20. That is, the link lever 17 is rotatably held by the damper holding member 20. The rotation center shaft 30 of this embodiment is the second rotation center shaft. The rotation center shaft 30 may be fixed to the damper holding member 20, and the link lever 17 may be rotatably held by the rotation center shaft 30. That is, the link lever 17 may be rotatably held by the damper holding member 20 via the rotation center shaft 30.

  The link lever 17 amplifies the operation amount of the second lever 16 and transmits it to the fluid damper 13. That is, the link lever 17 accelerates the operation of the second lever 16 and transmits it to the fluid damper 13. The lower end of the second lever 16 is engaged with the right end of the link lever 17 from above. At the lower end of the second lever 16, a recess that engages with the right end of the link lever 17 is formed 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 link lever 17 from above.

  As shown in FIG. 3, the action point of the link lever 17 on which the force from the fluid damper 13 acts is defined as a first action point 17a, and the force of the link lever 17 from the second lever 16 (that is, the second hinge member). 6), the distance L1 between the first action point 17a and the axis of the rotation center shaft 30 is equal to the second action point 17b. Is longer than the distance L2 from the axis center of. Specifically, the distance L1 is twice or more the distance L2. In this embodiment, the distance L1 is about twice the distance L2.

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

(Main effects of this embodiment)
As described above, in this embodiment, the hinge 1 includes the link lever 17 for amplifying the rotation amount of the second hinge member 6 with respect to the first hinge member 5 and transmitting the amplified rotation amount to the fluid damper 13. Therefore, in the present embodiment, it is possible to increase the operation amount of the fluid damper 13 when the second hinge member 6 rotates with respect to the first hinge member 5. Therefore, in the present embodiment, even if the relatively small and inexpensive fluid damper 13 having a low cushioning effect in which the case body and the piston rod are made of resin is used, the rotation of the second hinge member 6 relative to the first hinge member 5 is prevented. It becomes possible for the fluid damper 13 to obtain the cushioning force required to appropriately alleviate the dynamic motion. That is, in the present embodiment, it is possible to use the fluid damper 13 that is relatively small and inexpensive, while appropriately mitigating the rotational movement of the second hinge member 6 with respect to the first hinge member 5.

  In the present embodiment, the hinge 1 uses the first lever 15 for transmitting the biasing force of the compression coil spring 12 to the swing shaft 10 and the rotational movement of the second hinge member 6 with respect to the first hinge member 5 to the fluid damper 13. The link lever 17 amplifies the operation amount of the second lever 16 and transmits it to the fluid damper 13. When the rotational movement of the second hinge member 6 with respect to the first hinge member 5 is transmitted to the fluid damper 13 via the first lever 15 and the link lever 17, the second hinge member 6 with respect to the first hinge member 5 is moved. It is difficult to freely set the biasing force of the compression coil spring 12 that acts on the second hinge member 6 and the buffer force of the fluid damper 13 that acts on the second hinge member 6 at each pivot position, but in the present embodiment, By using the lever 15 and the second lever 16, the biasing force of the compression coil spring 12 acting on the second hinge member 6 and the second hinge member 6 are applied to the second hinge member 6 at each rotational position of the second hinge member 6. It is possible to set the acting buffer force of the fluid damper 13 relatively freely.

  In the present embodiment, the second swing shaft 11 that is arranged parallel to the rotation center shaft 7 and the swing shaft 10 and that rotates together with the second hinge member 6 with respect to the first hinge member 5 includes the second swing shaft 11 and the second swing shaft 11. The upper end of the lever 16 is rotatably connected. Therefore, in the present embodiment, the rotation operation 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 this embodiment, the link lever 17 is rotatably held by the damper holding member 20 that holds the fluid damper 13. Therefore, in this embodiment, in addition to the damper holding member 20, it is not necessary to separately provide a member for holding the link lever 17. Therefore, in this embodiment, the configuration of the hinge 1 can be simplified.

  In this embodiment, the link lever 17 is rotatable about the front-rear direction as the axis of rotation. Therefore, in this embodiment, the hinge 1 can be downsized in the front-rear direction as compared with the case where the link lever 17 is rotatable about the left-right direction as the rotation axis direction. That is, the hinge 1 can be thinned. Further, in the present embodiment, since the fluid damper 13 is arranged below the compression coil spring 12, compared with the case where the fluid damper 13 is arranged on the inner peripheral side of the compression coil spring 12, the front and rear of the hinge 1 are compared. It is possible to reduce the thickness in the direction. That is, in this embodiment, the hinge 1 can be thinned.

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

  Further, in the present embodiment, the contact portion 18b of the brake member 18 comes into contact with the first lever 15 by the biasing force of the compression coil spring 12, so the compression coil spring 12 for biasing the swing shaft 10 is used to It becomes possible to stop 15 at a predetermined position. Therefore, in this embodiment, the configuration of the hinge 1 can be simplified as compared with the case where a spring member for contacting the contact portion 18b with the first lever 15 is provided in addition to the compression coil spring 12. Become. Further, in the present embodiment, the contact portion 18b contacts the first lever 15 by the biasing force of the compression coil spring 12 for biasing the swing shaft 10, so that the contact pressure of the contact portion 18b with respect to the first lever 15 is increased. It will be possible.

(Other embodiments)
The embodiment described above is an example of a preferred embodiment of the present invention, but the present invention is not limited to this, 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 so that the piston rod of the fluid damper 13 projects upward. In this case, the lower end surface of the case body of the fluid damper 13 is in contact with the left end portion of the link lever 17 from above. Further, in the above-described embodiment, the fluid damper 13 may be a rotary fluid damper. Furthermore, 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 an air damper whose fluid chamber is filled with air.

  In the above-described embodiment, the fluid damper 13 may be wholly or partially protruded outside the left and right sides of the two side surfaces 5a. Further, in the above-described embodiment, the fluid damper 13 may be arranged side by side with the compression coil spring 12 in the left-right direction, or may be arranged on the inner peripheral side of the compression coil spring 12. Further, in the above-described embodiment, the second lever 16 may be arranged on the right side of the side surface portion 5a arranged on the right side, or may be arranged on the left side of the side surface portion 6a arranged on the right side.

  In the above-described embodiment, the first action point 17a is arranged on the left side of the rotation center shaft 30 and the second action point 17b is arranged on the right side of the rotation center shaft 30, but it is arranged on the left side of the rotation center shaft 30. The first action point 17a and the second action point 17b may be arranged. In this case, for example, the rotation center shaft 30 is arranged on the right side of the side surface portion 5a arranged on the right side. Further, in this case, for example, the fluid damper 13 is arranged so that the piston rod of the fluid damper 13 projects upward, and the left end portion of the link lever 17 contacts the piston rod of the fluid damper 13 from above. ing.

  In the above-described embodiment, the link lever 17 may be rotatable with the left-right direction as the axis of rotation. In this case, for example, the fluid damper 13 is wholly or partially disposed on the front side of the front end of the side surface portion 5a. In the above-described embodiment, the distance L1 between the first action point 17a and the axis of the rotation center shaft 30 is longer than the distance L2 between the second action point 17b and the axis of the rotation center shaft 30, and , Less than twice the distance L2.

  In the above-described embodiment, the swing shaft 10 may be used to regulate the rotation range of the second hinge member 6 with respect to the first hinge member 5. Further, in the above-described embodiment, the swing shaft 10 is used to restrict the rotation range of the second hinge member 6 to one side in the rotation direction of the second hinge member 6 with respect to the first hinge member 5, and The two swing shafts 11 may be used to regulate the turning range of the second hinge member 6 toward the other side in the turning direction of the second hinge member 6.

  In the above-described embodiment, the first lever 15 may transmit the rotational movement of the second hinge member 6 with respect to the first hinge member 5 to the fluid damper 13. That is, the link lever 17 may amplify the operation amount of the first lever 15 and transmit it to the fluid damper 13. In this case, the hinge 1 may not include the second lever 16 and the second swing shaft 11. Further, in this case, for example, the fluid damper 13 is arranged so that the piston rod of the fluid damper 13 protrudes upward, and the lower end of the first lever 15 is arranged from the upper side on the right side of the rotation center shaft 30. While being in contact with the link lever 17, the piston rod of the fluid damper 13 is in contact with the link lever 17 from below.

  In the above-mentioned form, the upper end of the second lever 16 may be rotatably connected to the second hinge member 6. In this case, the hinge 1 may not include the second swing shaft 11. In this case, the upper end of the second lever 16 may be directly connected to the second hinge member 6 or may be connected to the second hinge member 6 via a predetermined member. . Further, in the above-described embodiment, the fluid damper 13 may be directly attached to the first hinge member 5, or the link lever 17 may be directly rotatably held by the first hinge member 5. good.

  In the above-mentioned form, the rotatable angle of the second hinge member 6 with respect to the first hinge member 5 may exceed 90 °. Further, in the above-described embodiment, the swing shaft 10 may be formed integrally with the second hinge member 6, or the second swing shaft 11 may be formed integrally with the second hinge member 6. good. Further, in the above-described form, 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 brake member 23 is not generated. Moreover, in the above-mentioned form, the hinge 1 may not be provided with the brake member 18, and may not be provided with the brake member 23.

1 Hinge (Hinge with damper)
5 1st hinge member 6 2nd hinge member 7 Rotation center axis 10 Swing shaft 11 2nd swing shaft 12 Compression coil spring (spring member)
13 fluid damper 15 1st lever 16 2nd lever 17 link lever 17a 1st action point 17b 2nd action point 18 brake member 18a supported part 18b contact part 19 support member 20 damper holding member 30 rotation center axis (second rotation Center axis)
L1 distance between the first action point and the axis of the second rotation center axis L2 distance between the second action point and the axis of the second rotation center axis X axial direction of the rotation center axis Y second orthogonal direction Z Orthogonal direction Z1 First direction Z2 Second direction

Claims (11)

  A first hinge member and a second hinge member that are rotatably connected, a rotation center axis that is a rotation center of the second hinge member with respect to the first hinge member, and a parallel arrangement with the rotation center axis. And a swing shaft that rotates together with the second hinge member with respect to the first hinge member, and the swing shaft toward one side in a rotation direction of the second hinge member with respect to the first hinge member. A spring member for urging the first hinge member, a fluid damper for relaxing the rotational movement of the second hinge member with respect to the first hinge member, and an amplification amount of the second hinge member with respect to the first hinge member. And a link lever for transmitting the fluid to the fluid damper. The link lever is a rotation lever that is rotatable about a second rotation center axis,
When the action point of the link lever on which the force from the fluid damper acts is a first action point, and the action point of the link lever on which the force from the second hinge member acts is a second action point,
The distance between the first action point and the axis of the second rotation center shaft is longer than the distance between the second action point and the axis of the second rotation center shaft. The hinge with a damper according to claim 1.   The distance between the first action point and the axis of the second rotation center shaft is twice or more the distance between the second action point and the axis of the second rotation center shaft. The hinge with damper according to claim 2. When a direction orthogonal to the axial direction of the rotation center axis is an orthogonal direction and a direction orthogonal to the axial direction of the rotation center axis and the orthogonal direction is 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 hinge with a damper according to any one of claims 1 to 3, wherein the link lever is rotatable about the second orthogonal direction as an axial direction of rotation. A first lever for transmitting the urging force of the spring member to the swing shaft, and a second lever for transmitting the rotational movement of the second hinge member with respect to the first hinge member to the fluid damper. Prepare,
The hinge with a damper according to claim 1, wherein the link lever amplifies an operation amount of the second lever and transmits the amplified operation amount to the fluid damper. A second swing shaft that is disposed in parallel with the rotation center shaft and the swing shaft and that rotates together with the second hinge member with respect to the first hinge member;
The hinge with a damper according to claim 5, wherein one end of the second lever is rotatably connected to the second swing shaft.   7. The hinge with damper according to claim 1, wherein the fluid damper is a direct-acting fluid damper.   The hinge with a damper according to any one of claims 1 to 7, further comprising: a resin damper holding member that holds the fluid damper and is fixed to the first hinge member.   9. The hinge with a damper according to claim 8, wherein the link lever is rotatably held by the damper holding member. The spring member is a compression coil spring,
When a direction orthogonal to the axial direction of the rotation center axis is an orthogonal direction, one of the orthogonal directions is a first direction, and a direction opposite to the first direction is a second direction,
The second hinge member is connected to the first hinge member at the first direction end side of the first hinge member,
The compression coil spring is arranged on the second direction side with respect to the rotation center axis and the swing axis,
10. The hinge with damper according to claim 1, wherein the fluid damper is arranged on the second direction side with respect to the compression coil spring. A first lever for transmitting the biasing force of the spring member to the swing shaft; a brake member that comes into contact with the first lever at a predetermined contact pressure; and a support member that supports the brake member,
The spring member is a compression coil spring,
When a direction orthogonal to the axial direction of the rotation center axis is an orthogonal direction, one of the orthogonal directions is a first direction, and a direction opposite to the first direction is a second direction,
The second hinge member is connected to the first hinge member at the first direction end side of the first hinge member,
The compression coil spring is arranged on the second direction side with respect to the rotation center axis and the swing axis,
The brake member includes a supported portion supported by the supporting member, a contact portion arranged along the first lever and connected to the supported portion, and arranged on the second direction side of the compression coil spring. ,
The supported portion is supported by the support member from the second direction side and is biased by the compression coil spring from the first direction side,
The hinge with a damper according to any one of claims 1 to 10, wherein the contact portion comes into contact with the first lever by an urging force of the compression coil spring.

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