CN111088915B

CN111088915B - Fluid damper, hinge and refrigerator

Info

Publication number: CN111088915B
Application number: CN201811236628.6A
Authority: CN
Inventors: 大岛雄希; 马伟涛
Original assignee: Nidec Sankyo Zhejiang Corp; Nidec Sankyo Corp
Current assignee: Nidec Sankyo Zhejiang Corp; Nidec Sankyo Corp
Priority date: 2018-10-23
Filing date: 2018-10-23
Publication date: 2021-09-24
Anticipated expiration: 2038-10-23
Also published as: CN111088915A

Abstract

A fluid damper, a hinge having a fluid damper, and an ice bin having a fluid damper, the fluid damper comprising: a housing; and a rotor provided in the housing so as to be rotatable between a fully open position and a fully closed position, a fluid chamber being formed between an inner peripheral surface of the housing and an outer peripheral surface of the rotor, the fluid chamber including an open-side end surface, a radial surface, and a closed-side end surface that are continuous in a rotational direction of the rotor, and a working fluid being filled in the fluid chamber, wherein a reserved space is present between the rotor and the closed-side end surface of the fluid chamber at the fully closed position. According to the fluid damper of the present invention, at the fully closed position, there is a reserved space between the rotor and the closed-side end face of the fluid chamber. Thus, even when the damper is closed immediately after being opened from the full-close position, the working fluid is present in the reserve space, and therefore the fluid damper can sufficiently exhibit the damping action.

Description

Fluid damper, hinge and refrigerator

Technical Field

The invention relates to a fluid damper, a hinge with the fluid damper and an ice chest with the fluid damper.

Background

Conventionally, a fluid damper is often used to prevent noise from being generated by a violent collision with the cabinet body when the cabinet lid is closed.

The fluid damper generally includes a housing having a bottomed cylindrical portion with one end open and a lid portion closing an open end of the bottomed cylindrical portion, and a rotor rotatably provided in the housing and having a rotary shaft and a movable valve element, a fluid chamber being formed between the bottomed cylindrical portion, the lid portion, and the rotor, and a working fluid being filled in the fluid chamber.

In the fluid damper, when the rotary shaft is rotated in the first direction and the valve element is in the closed state, the working fluid is compressed to apply a load to the rotary shaft, whereas when the rotary shaft is reversed in the second direction and the valve element is in the open state, the fluid passes through the valve element, and thus no load is applied to the rotary shaft.

According to the above characteristics, for example, by fixing the rotor of the fluid damper to the cabinet lid and fixing the casing of the fluid damper to the cabinet body, when the cabinet lid is closed, the resistance generated by the fluid damper can be used to prevent the cabinet lid from closing too fast, thereby preventing the cabinet lid from colliding violently with the cabinet body and generating noise, and when the cabinet lid is opened, the fluid damper does not generate resistance, thereby enabling the cabinet lid to be opened fast.

In the prior art, for example, when the refrigerator cover is just opened, the refrigerator cover may be closed again by losing hands due to wet slip and the like. In this case, since almost all of the fluid in the fluid damper is concentrated on the opening side of the fluid chamber, the damping action is not exerted, and the refrigerator lid collides with the refrigerator main body to generate noise.

Disclosure of Invention

The present invention has been made to solve the above-described problems, and an object of the present invention is to provide a fluid damper that can sufficiently exhibit a damping action even when the fluid damper is closed immediately after being opened from a fully closed position. In addition, the invention also aims to provide a hinge with the fluid damper. In addition, the invention also aims to provide an ice chest with the fluid damper.

In order to achieve the above object, the present invention provides a fluid damper comprising: a housing; and a rotor provided in the housing so as to be rotatable between a fully open position and a fully closed position, a fluid chamber being formed between an inner peripheral surface of the housing and an outer peripheral surface of the rotor, the fluid chamber including an open-side end surface, a radial surface, and a closed-side end surface that are continuous in a rotational direction of the rotor, and a working fluid being filled in the fluid chamber, wherein a reserved space is present between the rotor and the closed-side end surface of the fluid chamber at the fully closed position.

According to the fluid damper of the present invention, at the fully closed position, there is a reserved space between the rotor and the closed-side end face of the fluid chamber. Thus, even when the damper is closed immediately after being opened from the full-close position, the working fluid is present in the reserve space, and therefore the fluid damper can sufficiently exhibit the damping action.

Further, in the fluid damper of the above-described configuration, it is preferable that the rotor includes: a rotor body portion having a shaft portion and a valve element holding portion protruding radially outward from the shaft portion; and a valve element that is rotatably held by the valve element holding portion, and that is separated from the closed end surface of the fluid chamber at the fully closed position.

According to the fluid damper configured as described above, the valve element holding portion is separated from the closed end surface of the fluid chamber at the fully closed position. Thus, the reserve space can be formed by a simple structure, contributing to reduction in manufacturing cost.

In the fluid damper of the above configuration, it is preferable that a part of the inner peripheral surface of the housing constitutes a contact surface that contacts the rotor body portion, and a recess portion that is recessed outward in the radial direction of the rotor so as to form the fluid chamber together with the rotor is formed in a portion of the housing where the contact surface is not formed.

According to the fluid damper of the above configuration, the recessed portion recessed toward the radial outside of the rotor forms the fluid chamber together with the rotor. This enables the formation of a sufficiently large fluid chamber with a simple structure, and contributes to reduction in manufacturing cost while ensuring a sufficient damping effect.

In the fluid damper configured as described above, it is preferable that the concave portion has a fan shape having a center of curvature of the center of the rotor body portion.

According to the fluid damper of the above configuration, the rotor smoothly rotates in the recess to exert the damping action.

In the fluid damper configured as described above, the concave portion preferably has a fan shape with a central angle of 120 °.

According to the fluid damper of the above configuration, it is possible to contribute to reduction of the internal space of the housing while ensuring a sufficient damping effect, thereby achieving miniaturization of the fluid damper.

In the fluid damper of the above configuration, it is preferable that the valve body holding portion has a groove, and the valve body has: a rotation center portion rotatably received in the groove; and a first protruding portion that protrudes from the rotation center portion toward a radially outer side of the rotor main body portion.

According to the fluid damper configured as described above, the first projecting portion of the valve body projects from the rotation center portion toward the radially outer side of the rotor main body portion. Thus, the first protrusion compresses the working fluid, and the damping action can be reliably exerted.

In the fluid damper of the above configuration, it is preferable that the valve element holding portion further includes a projection located radially outward of the rotor main body portion from the recess, and a recess formed in a portion of the first projecting portion that is connected to the rotation center portion and faces the projection, the recess being formed so as to be capable of fitting with the projection.

According to the fluid damper of the above-described structure, the recess of the first projecting portion can be fitted with the projection of the spool holding portion. This prevents the valve element from falling out of the recess of the valve element holding portion due to the reaction force of the working fluid, and contributes to more reliably exhibiting the damping action.

In the fluid damper configured as described above, it is preferable that the valve body further includes a second projection projecting from the first projection toward the fully open position.

According to the fluid damper of the above configuration, the valve body further includes the second projecting portion projecting from the first projecting portion toward the fully open position side. Thus, when the working fluid is compressed, the second projecting portion is brought into contact with the tip end of the valve element holding portion, whereby the valve element can be further prevented from falling out of the recess of the valve element holding portion by the reaction force of the working fluid, and the damper action can be more reliably exhibited.

In the fluid damper configured as described above, it is preferable that the second projecting portion is tapered toward the fully open position side from the first projecting portion.

According to the fluid damper of the above structure, it is helpful to prevent the second protrusion from obstructing the flow of the working fluid when opened.

Further, in order to achieve the above object, the present invention provides a hinge having a first hinge member and a second hinge member pivotally connected, and further having the above fluid damper, the first hinge member being fixed to a rotor of the fluid damper, and the second hinge member being fixed to a housing of the fluid damper.

Further, to achieve the above object, the present invention provides an ice chest comprising: a main body; a cover body; and a hinge pivotally connecting the body and the cover, the hinge comprising: the above-described fluid damper; and a first hinge member and a second hinge member pivotally connected, the first hinge member being fixed to the main body and the rotor of the fluid damper, the second hinge member being fixed to the cover and the case of the fluid damper.

(effect of the invention)

Drawings

FIG. 1 is a perspective view schematically showing the structure of an ice chest according to an embodiment of the present invention.

FIG. 2A is a schematic view of the connection of the hinge to the main body and the lid of the ice chest, showing the lid closed relative to the main body.

FIG. 2B is a schematic view showing the connection relationship between the hinge and the main body and the lid of the ice chest, and showing the state where the lid is opened with respect to the main body.

FIG. 3A is a partial perspective view schematically illustrating the structure of a hinge included in an ice chest of an embodiment of the present invention.

FIG. 3B is a partial perspective view schematically showing the structure of a hinge included in an ice chest according to an embodiment of the present invention, wherein a part of components such as a rotor is not shown.

Fig. 4A is a schematic axial view of the fluid damper according to the embodiment of the present invention with a cover removed.

Fig. 4B is a partially enlarged view schematically showing a valve body and a valve body holding portion of the fluid damper according to the embodiment of the present invention.

Fig. 5 is a partially enlarged view schematically showing a valve body and a valve body holding portion of a fluid damper according to a modification of the embodiment of the present invention.

(symbol description)

1 hinge

3 fluid damper

4 first hinge Member

4a first plate-like part

4b first base

4e first through hole

4f locking groove

5 second hinge Member

5a second plate-like part

5b second base

5c second through hole

5d third through hole

5e holding part

6 center axis of rotation

61 center shaft body

62 annular friction part

9 casing

9a inner peripheral surface

9a1 contact surface

10 rotor

10a outer peripheral surface

11 rotor body part

11a shaft part

11b valve body holding part

11b1 groove

11b2 first projection

11b3 second projection

12 valve core

12a center of rotation

12b first projection

12b1 depression

12b2 projection

12c second projection

15 locking pin

17 screw

22 torsion coil spring

22a hook part

BD main body

Center of C shaft part

CP recess

CV cover

FC full close position

FO full on position

LC fluid chamber

Open end face of LC1

Radial LC2 surface

LC3 closed end face

S headspace

Detailed Description

An ice chest according to an embodiment of the present invention will be described with reference to fig. 1 to 5, in which fig. 1 is a perspective view schematically showing a structure of an ice chest according to an embodiment of the present invention, fig. 2A is a schematic view showing a connection relationship between a hinge and a main body and a lid of the ice chest, and showing a state where the lid is closed with respect to the main body, fig. 2B is a schematic view showing a connection relationship between a hinge and a main body and a lid of the ice chest, and showing a state where the lid is opened with respect to the main body, fig. 3A is a partial perspective view schematically showing a structure of a hinge included in the ice chest according to an embodiment of the present invention, fig. 3B is a partial perspective view schematically showing a structure of a hinge included in the ice chest according to an embodiment of the present invention, in which a part of a component such as a rotor is omitted, fig. 4A partial perspective view schematically showing a fluid damper according to an embodiment of the present invention with the lid removed, and fig. 4B is a partial enlarged view schematically showing a valve core and a valve core holding portion of the fluid damper according to an embodiment of the present invention Fig. 5 is a partially enlarged view schematically showing a valve body and a valve body holding portion of a fluid damper according to a modification of the embodiment of the present invention.

Here, for convenience of explanation, three directions orthogonal to each other are set as an X direction, a Y direction, and a Z direction, one side of the X direction is set as X1, the other side of the X direction is set as X2, one side of the Y direction is set as Y1, the other side of the Y direction is set as Y2, one side of the Z direction is set as Z1, the other side of the Z direction is set as Z2, and an axial direction of a rotation center axis of the hinge coincides with the X direction.

As shown in fig. 1, 2A and 2B, the refrigerator has a substantially rectangular parallelepiped box shape and includes a main body BD and a lid CV connected to the main body BD via a hinge 1 so as to be rotatable about a horizontally extending axis for opening and closing.

Here, as shown in FIGS. 2A and 2B, the hinge 1 includes a first hinge member 4 and a second hinge member 5 rotatably connected to each other by a rotation center shaft 6, wherein the first hinge member 4 is provided on a main body BD of the refrigerator cabinet, and the second hinge member 5 is provided on a lid CV of the refrigerator cabinet. The hinge 1 further includes a fluid damper 3, and the fluid damper 3 generates resistance to the rotation of the second hinge member 5 with respect to the first hinge member 4, thereby preventing the damage of the main body BD of the refrigerator and the lid CV of the refrigerator due to the impact generated by the undamped opening and closing of the lid CV of the refrigerator. The hinge 1 further includes a rotation range restricting mechanism (not shown) for allowing the lid CV of the refrigerator cabinet to rotate between an open position (see the state of fig. 2B) and a closed position (see the state of fig. 2A) within an angular range of substantially 90 ° with respect to the main body BD of the refrigerator cabinet.

The structure of the hinge 1 will be specifically described below.

(integral Structure of hinge)

As shown in fig. 3A and 3B, the hinge 1 includes a first hinge member 4 and a second hinge member 5, the first hinge member 4 and the second hinge member 5 are rotatably connected by a rotation center shaft 6, and the rotation center shaft 6 is fixed to the first hinge member 4, a torsion coil spring 22 is wound around the rotation center shaft 6, the second hinge member 5 is rotatable with respect to the first hinge member 4 between a first position (corresponding to fig. 2B) and a second position (corresponding to fig. 2A), at the first position, the torsion coil spring 22 releases the rotation center shaft 6, and both end sides are restricted by the first hinge member 4 and the second hinge member 5, respectively, to generate an elastic restoring force to rotate the second hinge member 5 toward the second position, before the second hinge member 5 reaches the second position, the torsion coil spring 22 starts to embrace the rotation center shaft 6.

(Structure of first hinge Member)

As shown in fig. 3A and 3B, the first hinge member 4 includes two first plate-like portions 4a, the two first plate-like portions 4a being opposed to each other in the axial direction (i.e., the X direction) of the rotation center shaft 6, and first insertion holes 4e through which the rotation center shaft 6 is inserted are formed, respectively.

Here, the entire first plate-like portion 4a is substantially perpendicular to the X direction, a first insertion hole 4e is provided at an end portion of the first plate-like portion 4a on the Y1 direction side, and a locking groove 4f recessed radially outward from an inner peripheral surface of the first insertion hole 4e is provided.

Further, as shown in fig. 3A and 3B, the first hinge member 4 further includes a first base portion 4B, and the first base portion 4B connects the two first plate-like portions 4 a.

Here, the entire first base portion 4b is substantially perpendicular to the Z direction, and the Y1 direction side end portion of the first base portion 4b is located closer to the Y2 direction side than the Y1 direction side end portion of the first plate-shaped portion 4a, that is, the Y1 direction side end portion of the first plate-shaped portion 4a protrudes in the Y1 direction than the Y1 direction side end portion of the first base portion 4 b.

Further, although not shown, in the two first plate-like portions 4a, the first plate-like portion 4a on the X1 direction side has an abutting portion formed at the end portion on the Y1 direction side, and at the first position, the other end of the torsion coil spring 22 abuts against the abutting portion, and at the second position, the other end of the torsion coil spring 22 is separated from the abutting portion.

In addition, the material of the first hinge member 4 is not limited, and may be appropriately selected according to the circumstances, and for example, it is made of metal, resin, or the like.

(Structure of second hinge Member)

As shown in fig. 3A and 3B, the second hinge member 5 includes two second plate-like portions 5a, the two second plate-like portions 5a being opposed to each other in the axial direction of the rotation center shaft 6, and having second insertion holes 5c through which the rotation center shaft 6 is inserted, respectively.

Here, the entire second plate-like portion 5a is substantially perpendicular to the X direction, a second insertion hole 5c is provided at an end portion of the second plate-like portion 5a on the Y2 direction side, and a third insertion hole 5d into which a screw 17 for fixing the housing 9 of the damper 3 to the second hinge member 5 is inserted is provided at a position on the Y1 direction side of the second plate-like portion 5a with respect to the second insertion hole 5 c.

Further, as shown in fig. 3A and 3B, the second hinge member 5 further includes a second base portion 5B, and the second base portion 5B connects the two second plate-like portions 5 a.

Here, the entire second base portion 5b is substantially perpendicular to the Z direction, and the Y2 direction side end portion of the second base portion 5b is located closer to the Y1 direction side than the Y2 direction side end portion of the second plate-like portion 5a, that is, the Y2 direction side end portion of the second plate-like portion 5a projects toward the Y2 direction than the Y2 direction side end portion of the second base portion 5 b.

Further, as shown in fig. 3A and 3B, of the two second plate-like portions 5a, the two second plate-like portions 5a on the X1 direction side have holding portions 5e, and the holding portions 5e hold one ends of the torsion coil springs 22.

Here, the holding portion 5e has an engaging groove into which one end of the torsion coil spring 22 is engaged. Specifically, one end and the other end of the torsion coil spring 22 extend substantially in the YZ plane, and the one end of the torsion coil spring 22 has a hook 22a, and the hook 22a engages a part of the hook into the engaging groove of the holding portion 5e to hook the holding portion 5 e.

As shown in fig. 3A and 3B, the second hinge member 5 is disposed inside the first hinge member 4 in the axial direction of the rotation center shaft 6.

Here, in the axial direction of the rotation center shaft 6, the two second plate-like portions 5a of the second hinge member 5 are disposed inside the two first plate-like portions 4a of the first hinge member 4, the torsion coil spring 22 is located inside the two second plate-like portions 5a, and the fluid damper 3 is also located between the two second plate-like portions 5a and on the X2 direction side of the torsion coil spring 22.

In addition, the material of the second hinge member 5 is not limited, and may be appropriately selected according to the circumstances, and for example, it is made of metal, resin, or the like.

(Structure of rotating center shaft)

As shown in fig. 3A and 3B, the rotation center shaft 6 extends in the X direction, both end portions thereof penetrate the second insertion holes 5c of the two second plate-shaped portions 5a of the second hinge member 5 and the first insertion holes 4e of the two first plate-shaped portions 4a of the first hinge member 4, respectively, and a portion of the rotation center shaft 6 protruding outward from the first insertion holes 4e is crushed and caulked to the first plate-shaped portion 4a, thereby preventing the rotation center shaft 6 from coming off the first hinge member 4 and the second hinge member 5.

Here, the rotation center shaft 6 includes a center shaft main body 61 and an annular friction portion 62, the center shaft main body 61 is in a rod shape extending in the X direction, the annular friction portion 62 protrudes outward in the radial direction of the rotation center shaft 6 from the center shaft main body 61, and the torsion coil spring 22 is wound around the outer peripheral side of the annular friction portion 62. Specifically, the annular friction portion 62 is formed separately from the center shaft main body 61, and in the center shaft main body 61 of the rotation center shaft 6, the cross section perpendicular to the X direction of the portion located inside the two second plate-like portions 5a is substantially polygonal, and the annular friction portion 62 has a substantially polygonal center hole matching the cross sectional shape of the center shaft main body 61, and by inserting the center shaft main body 61 into the center hole of the annular friction portion 62, the annular friction portion 62 can be prevented from rotating relative to the center shaft main body 61.

As shown in fig. 2A and 2B, the rotation center shaft 6 further includes a locking pin 15, and the locking pin 15 is provided at least one end portion of the center shaft body 61, penetrates the center shaft body 61 in the radial direction of the center shaft body 61, and is locked in the locking groove 4f of the first plate-like portion 4a of the first hinge member 4, whereby the rotation center shaft 5 can be reliably prevented from rotating with respect to the first hinge member 4.

The material of the rotation center shaft 6 is not limited, and may be appropriately selected according to the circumstances, and for example, it is made of metal, resin, or the like (it is preferable to make the annular friction portion from a material that easily generates a large frictional force, and to make the center shaft main body from a material having a large strength).

(Structure of fluid damper)

As shown in fig. 4A, the fluid damper 3 includes: a housing 9; and a rotor 10 provided in the housing 9 so as to be rotatable between a fully open position FO (corresponding to fig. 2B) and a fully closed position FC (corresponding to fig. 2A), a fluid chamber LC including an open-side end surface LC1, a radial surface LC2, and a closed-side end surface LC3 which are continuous in a rotational direction of the rotor 10 is formed between an inner circumferential surface 9a of the housing 9 and an outer circumferential surface 10a of the rotor 10, and a working fluid (for example, oil, but not limited thereto) is filled in the fluid chamber LC, wherein a reserved space S is present between the rotor 10 and the closed-side end surface LC3 of the fluid chamber LC at the fully closed position FC.

Here, fig. 4A is an axial view of the fluid damper 3 as viewed in the X direction (i.e., the axial direction of the rotation center shaft 6), and shows a state where the rotor 9 is located at the fully closed position FC. For convenience of explanation of the internal structure of the fluid damper 3, fig. 4A removes a cover portion (not shown) that closes the internal space of the fluid damper 3 in the X direction.

According to the fluid damper 3 of the present invention, at the fully closed position FC, the reserve space S exists between the rotor 10 and the closed-side end face LC3 of the fluid chamber LC. Accordingly, even when the fluid damper 3 is closed immediately after being opened from the full close position FC, the valve element 12 described later receives a reaction force generated by compressing the working fluid due to the presence of the working fluid in the reserve space S, and further generates a closing resistance, and therefore, the fluid damper 3 can sufficiently exhibit a damping action.

With continued reference to fig. 4A, the internal structure of the fluid damper 3 will be described in detail. In the present embodiment, the rotor 10 includes: a rotor body 11, the rotor body 11 having a shaft portion 11a and a valve element holding portion 11b protruding radially outward from the shaft portion 11 a; and a valve body 12, the valve body 12 being held by the valve body holding portion 11b so as to be rotatable with respect to the valve body holding portion 11 b.

Here, the "fully open position FO" refers to: when the case 9 rotates to a fully opened position with respect to the rotor 10 along with the cover CV of the ice chest, the central axis of the valve body holding portion 11b substantially coincides with a broken line FO passing through the center C of the shaft portion 11a in fig. 4A; the "full-close position FC" refers to: when the case 9 is rotated to a fully closed position with respect to the rotor 10 along with the cover CV of the ice chest, the center axis of the valve body holding portion 11b substantially coincides with a broken line FC passing through the center C of the shaft portion 11a in fig. 4A. Note that the phrase "the existence of the reserve space S between the rotor 10 and the closed-side end surface LC3 of the fluid chamber LC at the fully closed position FC" specifically means that: at the fully closed position FC, the spool holding portion 11b is separated from the closed end surface LC3 of the fluid chamber LC. Thus, the reserved space S can be formed with a simple structure, contributing to reduction in manufacturing cost. The reserve space S may be formed by restricting the rotation of the housing 9 by the rotation range restricting mechanism of the hinge 1, or may be formed by directly abutting the valve element holding portion 11b of the rotor 10 against a portion of the closed-side end surface LC3 close to the shaft portion 11 a.

The internal space of the housing 9 will be described in detail below. As shown in fig. 4A, a part of the inner peripheral surface 9a of the housing 9 constitutes a contact surface 9a1 that contacts the rotor main body portion 11, and a recess CP that is recessed toward the radial outside of the rotor 10 is formed in a portion of the housing 9 where the contact surface 9a1 is not formed (i.e., mainly the open-side end surface LC1, the radial-direction end surface LC2, and the closed-side end surface LC3 of the fluid chamber LC), thereby forming the fluid chamber LC together with the rotor 10. Specifically, when viewed in the X (X2) direction, the concave portion CP has a substantially fan shape having the center C of curvature of the rotor main body portion 11 (shaft portion 11a) as a center of curvature, and the fan shape is mainly surrounded by the outer peripheral surface of the shaft portion 11a on the side of the direction Z2, and the open-side end surface LC1, the radial-direction surface LC2, and the closed-side end surface LC3 of the fluid chamber LC. Therefore, the fluid chamber LC is substantially a space of the recess CP excluding a part of the space occupied by the valve element holder 11b and the valve element 12. In the present embodiment, the central angle of the fan shape of the concave portion CP is substantially 120 °.

According to the fluid damper 3 of the present embodiment, the recessed portion CP recessed toward the radial outside of the rotor 10 forms the fluid chamber LC together with the rotor 10. This enables the formation of a sufficiently large fluid chamber LC with a simple structure, thereby contributing to a reduction in manufacturing cost while ensuring a sufficient damping effect. Further, forming the concave portion CP in a substantially fan shape helps the rotor 10 to smoothly rotate within the concave portion CP to exert a damping action. Further, the center angle of the fan shape is set to approximately 120 °, which contributes to a reduction in the internal space of the housing 9 while ensuring a sufficient damping effect, thereby realizing a reduction in the size of the fluid damper 3.

Although the case where the central angle of the concave portion CP is substantially 120 ° has been described above, the present invention is not limited to this. For example, the central angle of the concave portion CP may be set to any angle value greater than 120 ° or less than 120 ° according to actual use requirements.

Hereinafter, referring mainly to fig. 4B, specific configurations of the valve body holding portion 11B and the valve body 12 of the fluid damper 3 according to the embodiment of the present invention will be described in detail.

As shown in fig. 4B, the valve body holding portion 11B has a recessed groove 11B1, and the valve body 12 has: a rotation center portion 12a, the rotation center portion 12a being rotatably housed in the recess 11 b; and a first projecting portion 12b, the first projecting portion 12b projecting from the rotation center portion 12a toward the radially outer side of the rotor main body portion 11 a.

According to the fluid damper 3 of the present embodiment, the first projecting portion 12b of the valve 12 projects from the rotation center portion 12a toward the radial outside of the rotor main body portion 12 a. Thus, the first protrusion 12b compresses the working fluid, and the damping action can be reliably exerted.

Specifically, the valve body holding portion 11b includes a first protrusion 11b2 and a second protrusion 11b3 in addition to the groove 11b1, the first protrusion 11b2 is located radially outward of the rotor body portion 11a relative to the groove 11b1, and the second protrusion 11b3 is located radially inward of the rotor body portion 11a relative to the groove 11b 1. The groove 11b1 is substantially circular as viewed in the X direction with an opening toward the side of the closed-side end face LC3, and the first protrusion 11b2 and the second protrusion 11b3 are respectively formed so that the opening of the groove 11b1 gradually narrows toward the side of the closed-side end face LC3 to prevent the rotation center portion 12a of the valve body 12 from falling out of the groove 11b 1. The outer peripheral surface of the rotation center portion 12a of the valve body 12 is in close contact with the inner peripheral surface of the groove 11b1, so that the rotation center portion 12a can bring the entire valve body 12 to rotate smoothly while being always held in the groove 11b 1.

Further, a recess 12b1 is formed at a portion of the first protrusion 12b connected to the rotation center portion 12a and facing the first protrusion 11b2, and the recess 12b1 is formed to be capable of being fitted with the first protrusion 11b 2. When the rotor 10 rotates toward the fully closed position FC with respect to the housing 9 (i.e., when the cover CV of the ice bin is closed), the first projecting portion 12b is rotated toward the fully open position FO side by the reaction force of the working fluid, and the recess 12b1 and the first projection 11b2 are engaged with each other to prevent the first projecting portion 12b from further rotating toward the fully open position FO side, and further prevent the rotational center portion 12a of the valve body 12 from coming out of the recess 11b1, which contributes to further reliably exerting the damping action.

Further, a minute protrusion 12b2 is formed at a position of the first protrusion 12b facing the second protrusion 11b3, and when the rotor 10 rotates toward the fully open position FO relative to the housing 9 (i.e., when the cover CV of the ice chest is opened), the first protrusion 12b is rotated toward the fully closed position FC by the reaction force of the working fluid, and the protrusion 12b2 abuts against the second protrusion 11b3 to prevent the first protrusion 12b from further rotating toward the fully closed position FC, and further prevent the rotational center portion 12a of the valve body 12 from coming out of the recess 11b1, which contributes to more reliably exerting the damping action.

A specific structure of a valve body of a fluid damper according to a modification of the embodiment of the present invention will be described below with reference to fig. 5. In fig. 5, the same or similar components as those in fig. 4B are denoted by the same reference numerals, and redundant description is omitted.

In this modification, the configuration is the same as that of the above embodiment except that the valve body 12 further includes the second protrusion 12 c.

As shown in fig. 5, the second projecting portion 12c of the valve body 12 projects from the first projecting portion 12b toward the fully open position FO side (see fig. 4A as well). That is, the extending direction of the second protruding portion 12c is substantially perpendicular to the extending direction of the first protruding portion 12 b. Thus, when the working fluid is compressed, the second projecting portion 12c abuts against the tip end of the valve body holding portion 11b (specifically, the radially outer surface of the first projection 11b 2), whereby the valve body 12 can be prevented from falling out of the recessed groove 11b1 of the valve body holding portion 11b by the reaction force of the working fluid, and the damper action can be more reliably exhibited.

In the present modification, the second projecting portion 12c is tapered from the first projecting portion 12b toward the fully open position FO side. Thereby, it helps to prevent the second protrusion 12c from obstructing the flow of the working fluid when opened.

In the present invention, the embodiments may be freely combined, or may be appropriately modified or omitted within the scope of the present invention.

Claims

1. A fluid damper comprising: a housing; and a rotor provided in the housing so as to be rotatable between a fully open position and a fully closed position, a fluid chamber being formed between an inner peripheral surface of the housing and an outer peripheral surface of the rotor, the fluid chamber including an open-side end surface, a radial surface, and a closed-side end surface that are continuous in a rotational direction of the rotor, and being filled with a working fluid, characterized in that,

at the fully closed position, a head space exists between the rotor and the closed-side end face of the fluid chamber,

the rotor includes:

a rotor body portion having a shaft portion and a valve element holding portion protruding radially outward from the shaft portion; and

a valve body held by the valve body holding portion so as to be rotatable with respect to the valve body holding portion,

at the fully closed position, the spool holding portion is separated from the closed-side end surface of the fluid chamber.

2. The fluid damper as in claim 1,

a part of an inner peripheral surface of the housing constitutes a contact surface that contacts the shaft portion of the rotor,

a recess is formed in a portion of the housing where the contact surface is not formed, the recess being recessed toward a radially outer side of the rotor so as to form the fluid chamber together with the rotor.

3. The fluid damper as in claim 2,

the concave portion has a fan shape having a center of curvature of the center of the rotor body portion.

4. The fluid damper as in claim 3,

the central angle of the fan shape of the recess is 120 °.

5. The fluid damper as in claim 1,

the valve element holding portion has a groove formed therein,

the valve core is provided with:

a rotation center portion rotatably received in the groove; and

a first protruding portion that protrudes from the rotation center portion toward a radially outer side of the rotor main body portion.

6. The fluid damper as in claim 5,

the valve element holding part is also provided with a bulge which is closer to the radial outer side of the rotor main body part than the groove,

a recess is formed at a portion of the first protrusion connected to the rotation center portion and facing the protrusion, the recess being formed to be capable of being fitted with the protrusion.

7. The fluid damper as in claim 6,

the valve body further has a second projection projecting from the first projection toward the fully open position side.

8. The fluid damper as in claim 7,

the second projection is tapered toward the side of the fully open position from the first projection.

9. A hinge having a first hinge member and a second hinge member pivotally connected,

there is also a fluid damper as claimed in any of claims 1 to 8,

the first hinge member is fixed to a rotor of the fluid damper,

the second hinge member is fixed to a housing of the fluid damper.

10. An ice chest, comprising:

a main body;

a cover body; and

a hinge pivotally connecting the body and the cover,

the hinge includes:

the fluid damper as claimed in any one of claims 1 to 8; and

a first hinge member and a second hinge member pivotally connected,

the first hinge member is fixed to the main body and the rotor of the fluid damper,

the second hinge member is fixed to the cover and the case of the fluid damper.