CN211818856U - Damper and hinge comprising same - Google Patents

Abstract

A damper and a hinge including the damper can provide a greater damping force with a simple structure. The damper includes a housing (364) and a piston (362) that divides a fluid chamber into a collection chamber and a working chamber, and includes a main body portion (3624) that is formed with a large-diameter hole (36241A) that axially penetrates the main body portion and a small-diameter hole (36241B) that has a smaller diameter than the large-diameter hole, and a rod portion (3621) that is formed with a communication passage (36241C) that has one end that opens radially outward and communicates with the working chamber and the other end that communicates with the small-diameter hole, wherein a first stopper (3625) that closes the openings on one axial side of the large-diameter hole and the small-diameter hole when the piston moves toward the other axial side is provided on one axial end side of the rod portion so as to be axially movable, and that opens the openings on one axial side of the large-diameter hole and the small-diameter hole when the piston moves toward the other axial side.

Description

Damper and hinge comprising same

Technical Field

The utility model relates to a attenuator reaches hinge including this attenuator.

Background

Conventionally, a hinge with a damper is often used in a western-style toilet, a freezer, or the like, and the hinge is provided between a lid body and a main body portion to provide an appropriate damping force when the lid body closes the main body portion.

The damper is configured to include: a cylindrical housing made of metal and constituting a fluid chamber in which a working fluid flows; and a piston which is attached to the inside of the fluid chamber so as to be movable in an axial direction of the housing (hereinafter, sometimes simply referred to as an axial direction), and which divides the fluid chamber in the axial direction into a working chamber in which the working fluid is pressed to generate a damping force and a collection chamber into which the working fluid from the working chamber flows.

The body portion of the piston is formed in a bottomed cylindrical shape including a bottom wall portion and a cylindrical portion, and the bottom wall portion is formed with an orifice through which the working fluid flows into the accumulation chamber when the working fluid is pressed toward one side in the axial direction by the piston. However, the bottom wall portion of the piston has a limited thickness, and the length of the path through which the working fluid flows through the orifice is limited, and therefore the damping force generated by the damper may not be satisfactory.

Further, since the case is made of metal, the manufacturing cost may become high.

SUMMERY OF THE UTILITY MODEL

The present invention has been made in view of the above problems, and it is an object of the present invention to provide a damper and a hinge including the damper, which can provide a greater damping force with a simple structure.

In order to achieve the above object, a first aspect of the present invention provides a damper having a housing which forms a fluid chamber containing a working fluid, and a piston which has a main body part provided in the fluid chamber so as to be movable in an axial direction and a rod part having one end side connected to the main body part and the other end side protruding from the fluid chamber, wherein the main body part divides the fluid chamber in the axial direction into a collecting chamber and a working chamber on one side in the axial direction from the collecting chamber, and is formed with a large diameter hole, a small diameter hole and a communication passage which respectively axially penetrates the main body part, the small diameter hole having a diameter smaller than that of the large diameter hole, one end of the communication passage being opened radially outward so as to communicate with the working chamber, the other end of the communication passage communicating with the small diameter hole, a first stopper being provided at one end side of the rod part so as to be movable in the axial direction, the first stopper is provided to close the opening of one side in the axial direction of the large-diameter hole and the small-diameter hole when the piston moves toward one side in the axial direction, and to open the opening of one side in the axial direction of the large-diameter hole and the small-diameter hole when the piston moves toward the other side in the axial direction.

According to the above configuration, the body portion of the piston is provided with the communication passage which is provided so as to extend from the small-diameter hole to the radially outer side and communicate with the working chamber, and the one end side of the rod portion is provided with the first stopper which is provided so as to be movable in the axial direction and which closes the openings on one side in the axial direction of the large-diameter hole and the small-diameter hole when the piston moves to one side in the axial direction, whereby when the piston presses the working fluid to one side in the axial direction, the working fluid in the working chamber flows into the small-diameter hole first via the communication passage and then flows into the collection chamber from the small-diameter hole. The two-stage flow structure formed by the communication passage and the small-diameter hole can generate a larger damping force to the working fluid than in the related art, and thus a desired damping force can be easily satisfied.

The damper of the second aspect of the present invention is the damper of the first aspect of the present invention, wherein the communication path is formed as a notch extending straight from the small diameter hole toward the radial outside.

According to the above configuration, the communication path is formed as the slit linearly extending from the small-diameter hole to the radially outer side, whereby a larger damping force can be obtained with a simple configuration.

Further, since the communicating path is formed as a linearly extending slit, the slit can be easily formed in the manufacturing process.

The damper of the third aspect of the present invention is the damper of the first aspect of the present invention, wherein the communication path is formed as a cut groove extending from the small diameter hole toward the radial outside curve.

According to the above configuration, the communication passage is formed as the slit extending from the small-diameter hole to the radially outer side curve, so that the length of the communication passage can be extended as long as possible in the limited space, that is, the path through which the working fluid flows can be extended as long as possible in the limited space, and a sufficient damping force can be obtained.

The utility model discloses a damper of fourth aspect is on the basis of the damper of the second aspect or the third aspect of the utility model, the path hole is formed with major diameter portion and path portion from an axial side to the axially ascending opposite side, the radius ratio of path portion is little the radius of major diameter portion is little.

According to the above configuration, the small diameter portion is formed so as to have the large diameter portion and the small diameter portion from one side in the axial direction to the other side in the axial direction, and the radius of the small diameter portion is smaller than the radius of the large diameter portion, whereby the working fluid can be throttled by the small diameter portion, and the damping force against the working fluid can be further increased.

The damper of the fifth aspect of the present invention is the damper of the first aspect of the present invention, wherein the outer peripheral surface of the main body portion is formed with a groove over the entire circumference, the groove and the inner peripheral surface of the housing are provided with a seal ring therebetween.

According to the above configuration, the recessed groove is formed on the outer peripheral surface of the main body portion over the entire periphery, and the seal ring is interposed between the recessed groove and the inner peripheral surface of the housing, whereby the working chamber and the accumulation chamber can be reliably partitioned.

The utility model discloses a damper of sixth aspect is on the basis of the damper of the fifth aspect of the utility model, the sealing ring is the split ring.

According to the above configuration, the seal ring is formed as the open ring, whereby the open ring can be easily deformed in accordance with the deformation of the housing when the housing is deformed by an increase in pressure of the working fluid as compared with the closed ring, whereby a reduction in the damping force due to a large gap between the inner peripheral surface of the housing and the body portion of the piston can be reliably avoided.

The damper of the seventh aspect of the present invention is the damper of the first aspect of the present invention, wherein the main body portion of the piston is formed in a bottomed cylindrical shape, and the damper includes: a bottom wall portion formed with the large-diameter hole, the small-diameter hole, and the communication path; and a cylindrical portion, the other side of which in the axial direction is closed by the bottom wall portion.

The damper of the eighth aspect of the present invention is the damper of the seventh aspect of the present invention, wherein the fluid chamber is provided with a compression spring which is axially biased toward the piston.

According to the above configuration, the compression spring that is capable of biasing the piston in the axial direction is provided in the fluid chamber, and when the piston presses the working fluid toward one side in the axial direction, the compression spring generates a reaction force that prevents the piston from being further pressed, and the reaction force also acts as a damping force. Thereby, a larger damping force can be provided.

The damper of the ninth aspect of the present invention is the damper of any one of the first to third and fifth to eighth aspects, wherein the housing is made of resin.

According to the above configuration, since the case is made of resin, the manufacturing cost of the damper can be reduced as compared with the case where the case is made of metal.

In order to achieve the above object, the present invention provides a hinge, including: a first hinge part and a second hinge part rotatably connected by a rotation center shaft; an urging member that is supported between the first hinge member and the second hinge member and that applies a force that rotates the second hinge member with respect to the first hinge member; any one of the dampers of the first to ninth aspects; and an interlocking member that operates the damper in interlocking with rotation of the second hinge member relative to the first hinge member.

According to the above configuration, the damper is used for the connection between the first hinge member and the second hinge member, whereby the function of sufficiently damping the relative rotation between the first hinge member and the second hinge member can be exerted.

(effects of utility model)

According to the present invention, in the damper, the main body portion of the piston is provided with the communication passage which is provided to extend from the small-diameter hole to the radially outer side and communicate with the working chamber, and the one end side of the rod portion is provided with the first stopper in a manner movable in the axial direction, and the first stopper is provided to close the opening on one side in the axial direction of the large-diameter hole and the small-diameter hole when the piston moves toward one side in the axial direction, whereby when the piston presses the working fluid toward one side in the axial direction, the working fluid in the working chamber flows into the small-diameter hole via the communication passage first and then flows into the collecting chamber from the small-diameter hole. The two-stage flow structure formed by the communication passage and the small-diameter hole can generate a larger damping force to the working fluid than in the related art, and thus a desired damping force can be easily satisfied.

Drawings

FIG. 1 is an overall view schematically illustrating a hinged ice chest, wherein the hinge includes a damper according to an embodiment of the present invention.

FIG. 2 is a perspective view, partially in perspective, schematically illustrating a hinge including a damper according to an embodiment of the present invention, corresponding to a closed state of a lid of an ice chest relative to a main body of the ice chest.

Fig. 3 is an exploded perspective view schematically showing a hinge including a damper according to an embodiment of the present invention.

Fig. 4 is an exploded perspective view schematically showing a damper according to an embodiment of the present invention.

Fig. 5 is a view schematically showing a piston of a damper according to an embodiment of the present invention.

Fig. 6 is a view schematically showing a piston of a damper according to another embodiment of the present invention.

(symbol description)

1 refrigerator

100 refrigerator main body

200 cover

300 hinge

310 first hinge part

311 first side plate

3111 opening

3112 spacing groove

312 first base plate

320 second hinge member

321 second side plate

322 second base plate

330 center axis of rotation

341 first shaft

342 second shaft

350 force applying component

351 first rod

352 spiral spring

353 spring seat

360 damper

361 cover body

3611 cover component

3612 first clasp

3613 first washer

3614 buffer

3615 second washer

362 piston

3621 pole part

3622 third washer

3623 sealing ring

3624 body part

36241A large-diameter hole

36241B small diameter hole

36241C cutting groove

36241D cutting groove

3625 fourth washer

3626 fifth washer

3627 sixth washer

3628 second clasp

363 compression spring

371 second pole

381 guide piece

3811A trough part

382 storage part

383 support

360A hinge

400 hinge

CCW first direction

CW second direction

Detailed Description

Hereinafter, embodiments of a damper and a hinge including the damper according to the present invention will be described with reference to fig. 1 to 6. FIG. 1 is an overall view schematically illustrating a hinged ice chest, wherein the hinge includes a damper according to an embodiment of the present invention. FIG. 2 is a perspective view, partially in perspective, schematically illustrating a hinge including a damper according to an embodiment of the present invention, corresponding to a closed state of a lid of an ice chest relative to a main body of the ice chest. Fig. 3 is an exploded perspective view schematically showing a hinge including a damper according to an embodiment of the present invention. Fig. 4 is an exploded perspective view schematically showing a damper according to an embodiment of the present invention. Fig. 5 is a schematic view showing a piston of a damper according to an embodiment of the present invention. Fig. 6 is a view schematically showing a piston of a damper according to another embodiment of the present invention.

The utility model discloses a damper and hinge including this damper are applied to western style toilet bowl, refrigerator-freezer, automatic opening and closing door etc. usually in, and below to the condition that damper and hinge including this damper are applied to the refrigerator-freezer is exemplified and is explained in detail.

For convenience of explanation, three directions orthogonal to each other are referred to as an X direction, a Y direction, and a Z direction, one side of the X direction is referred to as X1, the other side of the X direction is referred to as X2, one side of the Y direction is referred to as Y1, the other side of the Y direction is referred to as Y2, one side of the Z direction is referred to as Z1, the other side of the Z direction is referred to as Z2, an extending direction of a lid of the freezer with respect to a rotation center line of the freezer body and an axial direction of a rotation center axis of the hinge are assumed to coincide with the X direction, and a height direction of the freezer is assumed to coincide with the Z direction.

(Integrated structure of refrigerator)

As shown in FIG. 1, the ice bin 1 comprises: an ice chest body 100, the volume of the ice chest body 100 is 100L-300L for example; and a lid 200, the lid 200 being rotatably connected to the ice chest body 100 by a hinge 300 and a hinge 400.

Here, the rotation center line of the lid 200 with respect to the refrigerator main body 100 coincides with the rotation center axis of the hinge 300 and the rotation center axis of the hinge 400; since the hinge 300 is a hinge with a damper and the hinge 400 is a hinge without a damper, and the hinge 400 is a conventional hinge, the hinge 300 will be mainly described in detail below, and the hinge 400 will not be described in detail.

(integral construction of hinge 300)

As shown in FIG. 2, the hinge 300 includes a first hinge member 310 (here secured to the ice chest body 100) and a second hinge member 320 (here secured to the lid 200), the first and second hinge members 310 and 320 being rotatably connected by a central axis of rotation 330.

Further, the hinge 300 includes: a force applying member 350, the force applying member 350 being supported between the first hinge member 310 and the second hinge member 320 and applying a force to rotate the second hinge member 320 with respect to the first hinge member 310; a damper 360 supported by the first hinge member 310 so as to be aligned with the urging member 350 in the extending direction (X direction in the illustrated example) of the rotation center axis 330, the damper 360 including a housing 364 (in which silicone oil as a working fluid is stored) and a piston 362 which are relatively movable in a predetermined direction (Z direction in the illustrated example) perpendicular to the rotation center axis 330; and an interlocking part 371 for operating the damper 360 in interlocking with the rotation of the second hinge member 320 with respect to the first hinge member 310. The first hinge member 310 is provided with a housing 382, and the housing 382 houses the damper 360 and contacts the outer peripheral surface of the housing 364 of the damper 360.

Here, the interlocking member is a second rod 371 which is rotatably connected to the second hinge member 320 and rotates with respect to the second hinge member 320 in accordance with the rotation of the second hinge member 320 with respect to the first hinge member 310, thereby approaching and pressing one of the housing 364 and the piston 362 (in the illustrated example, the piston 362) in the predetermined direction to generate a damping force in the damper 360 or separating from one of the housing 364 and the piston 362 (in the illustrated example, the piston 362) in the predetermined direction. Specifically, the hinge 300 includes a first shaft 341 (made of metal, for example) and a second shaft 342 (made of metal, for example), the first shaft 341 and the second shaft 342 being provided on the second hinge member 320 in parallel with the rotation center axis 330;

the urging member 350 is supported by the first hinge member 310 and the first shaft 341, and includes a first rod 351 extending in a direction perpendicular to the rotation center axis 330, and a coil spring 352 for applying a force for rotating the second hinge member 320 with respect to the first hinge member 310 in the first direction CCW around the rotation center axis 330 to the first shaft 341 via the first rod 351; further, a second rod 371 is rotatably connected to the second shaft 342 about the second shaft 342, and this second rod 371 is switched to a first position (i.e., a position where the refrigerator main body 100 is closed by the cover 200 of the refrigerator 1) as the second hinge member 320 rotates about the rotation center axis 330 with respect to the first hinge member 310 in a second direction CW opposite to the first direction CCW, and is switched to a second position (i.e., a position where the cover 200 of the refrigerator 1 opens the refrigerator main body 100) as the second hinge member 320 rotates about the rotation center axis 330 with respect to the first hinge member 310 in the first direction CCW, where the second rod 371 abuts against one of the housing 364 and the piston 362 (in the illustrated example, the piston 362) to generate a damping force to the damper 360, and where the second rod is separated from one of the housing 364 and the piston 362 (in the present embodiment) (that is, when the second hinge member 320 rotates about the rotation center axis 330 with respect to the first hinge member 310, the second rod 371 contacts one of the housing 364 and the piston 362 only within a predetermined range).

Further, the hinge 300 includes a guide 381, and the guide 381 guides the movement of the second rod 371 in the relative movement direction of the housing 364 and the piston 362, i.e., the above-mentioned preset direction.

(specific construction of the first hinge member 310 and the second hinge member 320)

Here, the first hinge member 310 is formed by press working a metal plate material.

Further, as shown in fig. 3, the first hinge member 310 includes: a pair of first side plates 311, the pair of first side plates 311 being opposed to each other in the extending direction of the rotation center shaft 330 and supporting both ends of the rotation center shaft 330; and a first bottom plate 312, the first bottom plate 312 connecting the pair of first side plates 311.

Further, an opening 3111 is provided in the first side plate 311 of the first hinge member 310 (in the illustrated example, the first side plate 311 on the X2 direction side), and the damper 360 is fitted into the opening 3111. Specifically, an opening 3111 is provided in the first side plate 311 on the side of the X2 direction, the opening 3111 is substantially rectangular in shape whose longitudinal direction coincides with the Z direction,

as shown in fig. 3, the damper 360 is housed in the housing 382 such that the rod 3621 of the piston 362 projects toward the Z1 direction side, and the housing 364 of the damper 360 is covered by the housing 382 surrounding the entire circumference; a guide 381 is integrally formed at the other end (end on the Z1 direction side in the illustrated example) of the housing 382, the guide 381 is fixed to the first side plate 311 on the X2 direction side by, for example, a screw or the like, and a groove portion 3811 extending in the Z direction is formed, and the groove portion 3811 is inserted so that the longitudinal direction of the second rod 371 substantially coincides with the Z direction, so as to guide the second rod 371 to move in the relative movement direction of the housing 364 and the piston 362.

The housing 382 is a resin case, and is formed in a substantially cylindrical shape as a whole, and is fitted into the opening 3111 so as to extend in the Z direction.

Further, at least one of the first side plates 311 is provided with a stopper groove 3112, and the stopper groove 3112 is formed in an arc shape centering on the rotation center axis 330, and into which the second shaft 342 is inserted, thereby restricting a rotation range of the second hinge member 320 with respect to the first hinge member 310 (in the illustrated example, the second hinge member 320 is rotatable by substantially 90 degrees with respect to the first hinge member 310, but not limited thereto); also, the stopper groove 3112 is provided: in a state where the second shaft 342 is located at an intermediate position in the circumferential direction of the stopper groove 3112 around the rotation center axis 330, a line connecting the rotation center axis 330 and the second shaft 342 is substantially perpendicular to the longitudinal direction of the second rod 371.

As shown in fig. 3, a support 383 (in the illustrated example, a substantially plate shape whose thickness direction coincides with the Z direction, but not limited thereto) is provided between the pair of first side plates 311, the first rod 351 penetrates the coil spring 352, one end (in the illustrated example, an end on the Z1 direction side) of the first rod 351 abuts the first shaft 341, the other end of the first rod 351 penetrates the support 383, a spring seat 353 is provided in the middle of the first rod 351, and both ends of the coil spring 352 are supported by the spring seat 353 and the support 383, respectively.

Here, the second hinge member 320 is formed by press working a metal plate material.

Further, as shown in fig. 3, the second hinge member 320 includes: a pair of second side plates 321, the pair of second side plates 321 opposing each other in the extending direction of the rotation center shaft 330 and supporting both ends of each of the rotation center shaft 330, the first shaft 341, and the second shaft 342; and a second bottom plate 322, the second bottom plate 322 connecting the pair of second side plates 321, at least a part of the damper 360, the urging member 350, and the pair of second side plates 321 being positioned between the pair of first side plates 311, respectively, and a relative movement direction of the housing 364 of the damper 360 and the piston 362 being substantially coincident with a longitudinal direction of the first rod 351 of the urging member 350 (the first rod 351 being capable of slightly swinging with respect to the first side plate 311 in a plane perpendicular to the rotation center axis 330).

As shown in fig. 2, the second rod 371 is provided between the first side plate 311 and the second side plate 321 on one side (the X2 direction side in the illustrated example) in the extending direction of the rotation center shaft 330. The first side plate 311 and the second side plate 321 on one side in the extending direction of the rotation center shaft 330 abut against the second rod 371 from both sides. The second rod 371 moves in the axial direction as the second shaft 342 moves in the stopper groove 3112 to press the piston 362 toward the Z2 side shown in fig. 2 to generate a damping force for the damper 360.

(Structure of damper 360)

Hereinafter, a specific structure of the damper 360 will be described with reference to fig. 4.

As shown in fig. 4, the damper 360 mainly includes a cover 361, a piston 362, a compression spring 363, and a case 364, wherein the cover 361 includes a cover member 3611, a first snap ring 3612, a first washer 3613, a cushion 3614, and a second washer 3615 in this order from a Z1 side to a Z2 side, the piston 362 includes a rod portion 3621, a third washer 3622, a seal ring 3623, a body portion 3624, a fourth washer 3625, a fifth washer 3626, a sixth washer 3627, and a second snap ring 3628 in this order from a Z1 side to a Z2 side, the case 364 has a cylindrical shape with a bottom and forms a fluid chamber for storing the working fluid, and a Z1 side opening is closed by the cover 361, and the compression spring 363 is provided between the sixth washer 3627 of the piston 362 and a bottom wall of the case 364.

For convenience of the following description, a region surrounded by the cover 361, the case 364, and the piston 362 on the Z1 side is referred to as a collecting chamber, and a region surrounded by the case 364 and the piston 362 on the Z2 side is referred to as a working chamber. In other words, the piston 362 divides a space formed by the cover 361 and the housing 364 into the accumulation chamber and the working chamber in the Z direction.

As shown in fig. 4, the rod portion 3621 includes a large diameter portion 3621A, a small diameter portion 3621B, and a tapered portion 3621C, wherein a stepped portion 3621D is formed at a junction between the large diameter portion 3621A and the small diameter portion 3621B, the stepped portion 3621D abuts against a Z1 side surface of the main body portion 3624 to determine a position of the rod portion 3621 in the axial direction with respect to the main body portion 3624, and a catch groove 3621E is formed at a junction between the small diameter portion 3621B and the tapered portion 3621C, the catch groove 3621E being engaged by the second catch 3628 to determine a position of the rod portion 3621 in the axial direction with respect to the main body portion 3624.

As shown in fig. 4 and 5, the body 3624 of the piston 362 has a bottomed cylindrical shape and includes: a bottom wall portion 36241, the bottom wall portion 36241 being disk-shaped and formed with seven large-diameter holes 36241a, one small-diameter hole 36241B and a communication passage 36241C, wherein seven large-diameter holes 36241a and one small-diameter hole 36241B are distributed in the bottom wall portion 36241 in a substantially circular shape; and a cylindrical portion 36242 in which the cylindrical portion 36242 extends from the bottom wall portion 36241 toward the Z2 side, and in which a groove 36242a is formed over the entire circumference on the outer circumferential surface, and the seal ring 3623 is fitted into the groove 36242 a. By fitting the seal ring 3623 into the groove 36242A and bringing the outer peripheral surface of the seal ring 3623 into close contact with the inner peripheral surface of the housing 364, the working chamber in which the compression spring 363 is housed can be sealed from the accumulation chamber (here, the clearance between the outer peripheral surface of the seal ring 3623 and the groove 36242A is small, and therefore, the influence of the clearance on the sealing performance of the working chamber is not considered).

As shown in fig. 4, the seal ring 3623 is an open ring in which a notch 3623A is formed in a part of the circumferential direction, and the notch 3623A is inclined with respect to the Z direction, so that the housing 364 is more easily deformed in accordance with the amount of deformation of the housing 364 when the housing 364 is deformed due to an increase in pressure of the working fluid, as compared with the case where the seal ring 3623 is a closed ring. Thus, when the internal pressure of the working chamber becomes high, the working fluid flows into the gap between the inner peripheral surface of the seal ring 3623 and the bottom surface of the recessed groove 36242a via the notch 3623A to urge the seal ring 3623 from the radially inner side. This can always maintain a good sealing state between the seal ring 3623 and the inner circumferential surface of the housing 364.

Thus, when the piston 362 presses the working fluid in the working chamber to the Z2 side, since a good sealing state is always maintained between the seal ring 3623 and the housing 364 (that is, the working chamber is always kept in a good sealing state with respect to the accumulation chamber), the pressure of the working fluid in the working chamber increases, and sufficient conditions for generation of the damping force are created.

As shown in fig. 5, in the bottom wall portion 36241 of the main body portion 3624 of the piston 362, the communication passage 36241C is a slit extending linearly from the small-diameter hole 36241B to the outside in the radial direction, and the depth of the slit is, for example, 0.5 mm.

The fourth washer 3625 is located on the Z2 side of the body portion 3624, and is provided to close the openings of the seven large-diameter holes 36241a and the one small-diameter hole 36241B when the piston 362 moves toward the Z2 side, and to open the seven large-diameter holes 36241a and the one small-diameter hole 36241B when the piston 362 moves toward the Z1 side. Specifically, the outer peripheral edge of the fourth washer 3625 is positioned on the outer peripheral side of the outer peripheral edges of the large-diameter holes 36241a and the small-diameter hole 36241B as viewed in the axial direction.

By providing the small-diameter hole 36241B and the communication passage 36241C in this manner, the path through which the working fluid flows to the accumulation chamber when the piston 362 presses the working fluid toward the Z2 side can be extended, and a greater damping force can be provided.

The small-diameter hole 36241B is formed in a stepped shape when viewed in the radial direction, and specifically, the small-diameter hole 36241B has a large diameter portion on the Z2 side and a small diameter portion on the Z1 side.

By forming the small diameter hole 36241B in a stepped shape including a large diameter portion and a small diameter portion in this manner, sufficient damping of the working fluid flowing from the working chamber to the accumulation chamber can be achieved.

Further, a compression spring 363 is housed in a fluid chamber formed by the housing 364, and when the piston 362 presses the working fluid toward the Z2 side, the compression spring 363 is compressed to generate a damping force that prevents the piston 362 from moving further toward the Z2 side. Thereby, a larger damping force can be provided.

In the present embodiment, the case 364 of the damper 360 is made of resin, so that the manufacturing cost can be reduced as compared with a case made of metal in the related art.

Although the embodiments of the present invention have been described above, the elements of the embodiments can be used in combination without departing from the spirit of the present invention, in addition to the technical means described in the embodiments.

In embodiment 1 described above, the notch 36241C in the bottom wall portion 36241 of the body portion 3624 of the piston 362 is formed so as to extend straight radially outward from the small diameter hole 36241B and communicate with the working chamber, but the present invention is not limited to this, and as shown in fig. 6, a notch 36241D that extends radially inward from the small diameter hole 36241B and then turns back to extend radially outward may be formed in the bottom wall portion 36241 of the body portion 3624 of the piston 362, and this notch 36241D surrounds the small diameter hole 36241B so as to be divided into seven groove portions and to be substantially rectangular.

By configuring the notch 36241D in the above manner, when the piston 362 presses the working fluid toward the Z2 side during operation of the damper 360A, the fourth washer 3625 blocks the large-diameter hole 36241a and the small-diameter hole 36241B of the bottom wall portion 36241 of the body portion 3624 of the piston 362 from the Z2 side to the Z1 side, and opens only the notch 36241D. As a result, the working fluid in the working chamber flows toward the accumulation chamber through the cutting groove 36241D and the small diameter hole 36241B due to the increase in pressure.

As a result, as in embodiment 1, the path through which the working fluid flows becomes longer than in the conventional art, and therefore, a larger damping force can be provided.

In the above embodiment, seven large-diameter holes and one small-diameter hole are formed in the bottom wall portion of the body portion of the piston, but the number of the large-diameter holes and the small-diameter holes may be appropriately adjusted as long as a predetermined damping force is obtained.

In embodiment 2, the notch of the communication path is formed in a substantially rectangular shape, but the present invention is not limited to this, and may be formed in another curved shape such as a substantially circular shape.

In the above embodiment, the seal ring is formed with one notch, but the present invention is not limited to this, and one or more notches may be formed.

In the above embodiment, the compression spring and the sixth washer supporting the compression spring are provided in the working chamber of the fluid chamber, but the present invention is not limited to this, and the compression spring and the sixth washer may not be provided.

Claims (10)

1. A damper having a housing which forms a fluid chamber containing a working fluid, and a piston which has a main body part provided in the fluid chamber so as to be movable in an axial direction and a rod part having one end connected to the main body part and the other end protruding from the fluid chamber, the main body part axially dividing the fluid chamber into a collecting chamber and a working chamber on one side in the axial direction from the collecting chamber,

a large-diameter hole, a small-diameter hole, and a communication passage, the large-diameter hole and the small-diameter hole penetrating the body in the axial direction, the small-diameter hole having a diameter smaller than that of the large-diameter hole, one end of the communication passage opening radially outward and communicating with the working chamber, the other end of the communication passage communicating with the small-diameter hole,

a first stopper is provided at one end side of the rod portion in an axially movable manner, the first stopper being provided to close an opening of one side in the axial direction of the large-diameter hole and the small-diameter hole when the piston moves toward one side in the axial direction, and to open the opening of one side in the axial direction of the large-diameter hole and the small-diameter hole when the piston moves toward the other side in the axial direction.

2. The damper of claim 1,

the communication path is formed as a slit extending linearly from the small-diameter hole toward the radial outer side.

3. The damper of claim 1,

the communication path is formed as a slit extending from the small-diameter hole toward a radially outer curve.

4. The damper of claim 2 or 3,

the small-diameter hole is provided with a large-diameter part and a small-diameter part from one side in the axial direction to the other side in the axial direction, and the radius of the small-diameter part is smaller than that of the large-diameter part.

5. The damper of claim 1,

a groove is formed in the outer peripheral surface of the body portion over the entire periphery thereof, and a seal ring is interposed between the groove and the inner peripheral surface of the housing.

6. The damper of claim 5,

the sealing ring is an open ring.

7. The damper of claim 1,

the body portion of the piston is formed in a bottomed cylindrical shape, and includes:

a bottom wall portion formed with the large-diameter hole, the small-diameter hole, and the communication path; and

a cylindrical portion, the other side of which in the axial direction is closed by the bottom wall portion.

8. The damper of claim 7,

a compression spring capable of applying force to the piston in the axial direction is provided in the fluid chamber.

9. The damper according to any one of claims 1 to 3, 5 to 8,

the housing is made of resin.

10. A hinge, comprising:

a first hinge part and a second hinge part rotatably connected by a rotation center shaft;

an urging member that is supported between the first hinge member and the second hinge member and that applies a force that rotates the second hinge member with respect to the first hinge member;

the damper of any one of claims 1 to 9; and

an interlocking member that operates the damper in interlocking with rotation of the second hinge member relative to the first hinge member.

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