WO2023171653A1

WO2023171653A1 - Damper device

Info

Publication number: WO2023171653A1
Application number: PCT/JP2023/008513
Authority: WO
Inventors: 淳斎藤; 幸一加藤
Original assignee: 株式会社パイオラックス
Priority date: 2022-03-10
Filing date: 2023-03-07
Publication date: 2023-09-14

Abstract

Provided is a damper device that makes it possible to reduce piston operation force when a piston moves in a return direction opposite to a damper braking direction. This damper device 10 includes a cylinder 20, a rod 30, a piston 40 provided with an annular groove 45, and a seal ring 50. The seal ring 50 includes a base 51, two inner diameter-side protrusions 53, 55, and an outer diameter-side protrusion 57. At least one of the inner diameter-side protrusions 53, 55 is in contact with the bottom surface 45a of the annular groove 45. The outer diameter-side protrusion 57 is a surface on the outer diameter side of the base 51 and protrudes in an annular shape so that a top section 57a of the outer diameter-side protrusion 57 is arranged at a position corresponding to the interval between the top sections 53a, 55a of the axially adjacent inner diameter-side protrusions 53, 55.

Description

damper device

The present invention relates to a damper device used, for example, for braking the opening and closing operations of a glove box of an automobile.

For example, a damper device is sometimes used in a car glove box to suppress the lid from opening suddenly and allow the lid to open slowly.

As such a damper device, Patent Document 1 below describes a housing, a piston rod that slides within the housing, a piston head provided at the front end of the piston rod, and an annular groove formed on the outer periphery of the piston head. An air damper assembly is described having a lip seal attached to the air damper assembly.

The lip seal includes a base, an inner lip that protrudes from the inner edge of one axial end of the base, contacts the bottom of the annular groove, protrudes from the outer edge of the one axial end of the base, and contacts the inside of the housing. It consists of an outer lip that comes into contact with the circumferential surface, and has a substantially U-shaped cross section. Further, the outer lip projects obliquely outward with respect to the inner lip, and normally, the tip of the outer surface of the outer lip partially abuts against the inner circumferential surface of the housing.

Japanese Patent Application Publication No. 8-277873

In the case of the air damper assembly of Patent Document 1, when the piston head moves in the return direction opposite to the damper braking direction, the piston rod may tilt with respect to the axis of the housing. In this case, since the piston head also inclines following the inclination of the piston rod, the outer lip outer surface of the lip seal attached to the annular groove comes into wide contact with the inner circumferential surface of the housing. As a result, the frictional resistance of the lip seal against the inner circumferential surface of the housing increases, which may increase the operating force of the piston head.

Therefore, an object of the present invention is to provide a damper device that can reduce the operating force of the piston when the piston moves in the return direction opposite to the damper braking direction.

In order to achieve the above object, the present invention provides a damper device that is attached between a pair of members that move closer to each other and applies a braking force when the pair of members move closer to each other or move away from each other, the damper device having an opening at one end. a cylinder provided with an annular groove; a rod movably inserted into the cylinder through the opening; a piston connected to the rod and having an annular groove formed on its outer periphery; and a seal ring that is pressed against the inner circumferential surface of the cylinder, and the seal ring has an annular base disposed in the annular groove and at least two seal rings protruding from the inner diameter side surface of the base. and an outer diameter side protrusion that protrudes from the outer diameter side surface of the base and comes into contact with the inner circumferential surface of the cylinder, and at least one of the inner diameter side protrusions is in contact with the bottom surface of the annular groove, and the outer diameter side protrusion is located on the outer diameter side surface of the base, at a position corresponding to between the tops of the axially adjacent inner diameter side protrusions. , characterized in that it protrudes in an annular shape such that the top of the outer diameter side protrusion is located.

In the present invention, the outer diameter side protrusion is a surface of the base on the outer diameter side, and the top of the outer diameter side protrusion is placed at a position corresponding to between the tops of the inner diameter side protrusions adjacent to each other in the axial direction. Since the seal ring protrudes in an annular shape so that , the operating force of the piston can be reduced.

1 is an exploded perspective view showing one embodiment of a damper device according to the present invention. It is a perspective view of the same damper device. It is an enlarged perspective view of the piston which constitutes the same damper device. FIG. 2 is an enlarged perspective view of a seal ring that constitutes the damper device. 5 is a cross-sectional view taken along the line of arrow BB in FIG. 4. FIG. 3 is a cross-sectional view taken along the line AA in FIG. 2, with the rod pulled out a predetermined length. FIG. FIG. 3 is an enlarged cross-sectional explanatory view of a main part of the damper device when the piston moves in the damper braking direction. FIG. 7 is an explanatory enlarged cross-sectional view of a main part of the damper device when the piston moves in the return direction opposite to the damper braking direction.

(One embodiment of a damper device)
DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of a damper device according to the present invention will be described below with reference to the drawings.

The damper device 10 shown in FIG. 1 is attached to a pair of members that move close to each other and separate from each other, and applies braking force when the pair of members approach or move away from each other. It can be used for braking a glove box, a lid, etc., which is attached to the opening of the provided storage part so as to be openable and closable. In the following embodiments, one member is a fixed body such as an instrument panel accommodating part, and the other member is a glove box, a lid, etc. that is attached to the opening of the fixed body so that it can be opened and closed. This will be explained as an opening/closing body.

As shown in FIG. 1, the damper device 10 of this embodiment includes a cylinder 20 having an opening 23 at one end, a rod 30 movably inserted into the cylinder 20, and a cylinder 20 connected to the rod 30. , a piston 40 having an annular groove 45 formed on its outer periphery, a seal ring 50 attached to the annular groove 45 of the piston 40, and a detachment prevention cap 60 attached to the opening 23 at one end of the cylinder 20. It mainly consists of Further, as shown in FIG. 6, when the piston 40 is inserted into the cylinder 20, the seal ring 50 is brought into pressure contact with the inner peripheral surface of the cylinder 20. A first chamber V1 (air chamber) is formed on the side in the insertion direction of the rod 30, and a second chamber V2 is formed on the side of the opening 23 of the cylinder 20.

In addition, in the following description, "one end" or "one end" means one end or one end of the damper device 10 on the damper braking direction side, and "the other end" or "other end" means the damper It means the other end or other end on the return direction side opposite to the braking direction. In addition, the "damper braking direction" in this embodiment means that the piston 40 moves away from the end wall 25 of the cylinder 20 (see FIG. 6), and the amount of the rod 30 pulled out from the opening 23 of the cylinder 20 increases. (See arrow F1 in FIG. 6). Furthermore, in this embodiment, the "return direction opposite to the damper braking direction" (hereinafter also simply referred to as "damper return direction") means that the piston 40 is close to the end wall 25 of the cylinder 20 and inside the cylinder 20. This means the direction in which the amount of pushing of the rod 30 increases (see arrow F2 in FIG. 6).

As shown in FIG. 1, the wall portion 21 of the cylinder 20 has an annular cross section perpendicular to its axial direction having a long axis and a short axis, and is wide on the long axis side and narrow on the short axis side. It has a thin cylindrical shape (a cylindrical shape with a thin box shape). More specifically, this wall portion 21 includes a pair of long-

axis wall portions

21a, 21a that extend linearly along the long-axis direction and are arranged parallel to each other, and these long-axis wall portions. It has a pair of short

axis wall portions

21b, 21b which connect both ends of the 21a and 21a and are curved in an arc shape. One end of the wall 21 in the axial direction is open, and an opening 23 is provided. Further, locking

holes

23a, 23a are formed in the long

axis wall portions

21a, 21a, which are disposed at the periphery of the opening 23 and are opposed to each other, respectively. Further, as shown in FIG. 6, an end wall 25 is disposed at the other end of the wall 21 in the axial direction (the end wall 25 is disposed on the opposite side of the wall 21 from the opening 23). The other end of the wall portion 21 is closed.

Further, from the outer surface of the end wall 25 and the outer periphery of the wall portion 21 from one end in the axial direction, a rotation support piece 27 having a rotation hole 27a formed therein is protruded, respectively. A rotation shaft (not shown) of one of the aforementioned members is rotatably inserted into the predetermined rotation hole 27a, so that the outer periphery of the cylinder 20 is rotatably connected to the one member. There is.

As shown in FIG. 1, the detachment prevention cap 60 has a rod insertion hole 61 formed in its center to allow insertion of the shaft portion 31 of the rod 30 while restricting its rotation. It can be inserted into the cylinder 20 with rotation restricted. Further, a plurality of locking protrusions 62 are protruded from predetermined locations on the outer periphery of the detachment prevention cap 60, and each locking protrusion 62 can be respectively locked in each corresponding locking hole 23a of the cylinder 20. (See FIG. 2), and a detachment prevention cap 60 is attached to the opening 23 of the cylinder 20 (see FIG. 6). The detachment prevention cap 60 comes into contact with the piston 40 when the rod 30 is pulled out to the maximum extent from the opening 23 of the cylinder 20, and prevents the rod 30 and the piston 40 from detaching from the cylinder 20.

Next, the rod 30 will be explained.

This rod 30 is movably inserted into the cylinder 20 through the opening 23 of the cylinder 20 and slides within the cylinder 20 in the axial direction of the cylinder 20.

As shown in FIG. 1, the rod 30 of this embodiment has a prismatic shaft portion 31 that extends in one direction. A connecting piece 33 having a connecting hole 33a is provided at one end in the longitudinal direction of this shaft portion 31. As shown in FIG. A connecting shaft (not shown) of the other member mentioned above is inserted into the connecting hole 33a, so that the rod 30 is rotatably connected to the other member.

Next, the piston 40 will be explained.

As shown in FIGS. 1 and 3, the piston 40 of this embodiment is connected to the other end of the rod 30 in the longitudinal direction, and has an annular groove 45 formed on its outer periphery. It is integrally formed.

Referring to FIGS. 6 and 7 together, this piston 40 has a first side wall portion 41 and a second side wall portion 42 that are arranged opposite to each other so as to be parallel to each other, and a connection that connects the both

side wall portions

41 and 42 to each other. It consists of a wall part 43. Each of the

side wall portions

41 and 42 has a shape that matches the inner peripheral shape of the wall portion 21 of the cylinder 20, that is, both side surfaces in the long axis direction are parallel to each other, and both side surfaces in the short axis direction are arcuate. Further, the connecting wall portion 43 has a similar shape in which the outer circumference thereof is smaller than the outer circumferences of the both

side wall portions

41 and 42.

Note that the surface of the first side wall portion 41 facing the second side wall portion 42 is referred to as the inner surface 41a of the first side wall portion 41, and the surface of the second side wall portion 42 facing the first side wall portion 41 is referred to as the inner surface 41a of the first side wall portion 41. This is the inner surface 42a of the side wall portion 42.

A space surrounded by the pair of

side walls

41 and 42 and the connecting wall 43 forms an annular groove 45. Further, the outer peripheral surface of the connecting wall portion 43 forms the bottom surface 45a of the annular groove 45. The bottom surface 45a is formed parallel to the axial direction of the piston 40 (the direction along the axis C of the piston 40).

Further, the axial proximal end portion of the rod 30 is connected to the outer surface (the surface opposite to the surface facing the second side wall portion 42) of the first side wall portion 41 disposed on one end side in the longitudinal direction of the piston 40. The piston 40 and the rod 30 are integrated.

Furthermore, as shown in FIGS. 6 and 7, a plurality of spaces K defined by a partition wall 46 are provided inside the

side walls

41, 42 and the connecting wall 43, and each space K has a The second side wall portion 42 side is open. Also, referring to FIG. 3, at a predetermined position of the first side wall part 41, here, at one end side in the axial direction of the first side wall part 41 and at the center position in the width direction, it communicates with a predetermined space K. An orifice 47 in the form of a small diameter round hole is formed. This orifice 47 allows the first chamber V1 and the second chamber V2 in the cylinder 20 to communicate with each other via the space K. Note that the damper braking force is adjusted by the flow resistance of the air passing through the orifice 47.

Furthermore, as shown in FIG. 3, a pair of

notch grooves

48, 48 formed by cutting out the first side wall portion 41 and the connecting wall portion 43 are provided at positions point symmetrical with respect to the axis C of the piston 40. formed at depth. This notch groove 48 forms an exhaust flow path that exhausts the air in the first chamber V1 to the second chamber V2 side when the piston 40 moves in the return direction F2 (this will be described later).

Next, the seal ring 50 will be explained with reference to FIGS. 4 and 5.

The seal ring 50 is made of an elastic material such as rubber or an elastomer, and is flexible and deformable. , at least two

inner diameter protrusions

53, 55 protruding from the outer diameter surface (hereinafter also simply referred to as the "outer diameter surface 51b") of the base 51; It has an outer diameter side protrusion 57 that presses against the inner circumferential surface of the cylinder 20. Note that the inner diameter side surface and the outer diameter side surface of the base portion 51 can also be referred to as an "inner circumferential surface" and an "outer circumferential surface", respectively.

The base portion 51 has an annular shape that matches the outer peripheral shape of the annular groove 45 of the piston 40. Further, the axial length W1 of the base 51, that is, the length between one end surface 51c and the other end surface 51d of the base 51 in the axial direction, is the axial width of the annular groove 45 (the inner surface 41a of the first side wall portion 41 and the The seal ring 50 is formed to be smaller than the length of the inner surface 42a of the second side wall portion 42, thereby allowing the seal ring 50 to move in the axial direction within the annular groove 45. Note that the inner circumferential surface of the cylinder 20 in this embodiment means the inner circumferential surface of the wall portion 21 that constitutes the cylinder 20, and this also applies in the following description.

4 and 5 show a state before the seal ring 50 is installed in the annular groove 45, that is, a free state before the seal ring 50 is pressed against the inner peripheral surface of the cylinder 20 and is deformed. has been done. In addition, in the following description of the shape, structure, and layout (position and arrangement of each part) of each part of the seal ring 50, unless otherwise specified, the shape, structure, and layout of the seal ring 50 in its free state are used. means.

In this embodiment, the inner protrusions are two protruding parts of the base 51 that protrude from both ends of the seal ring 50 in the axial direction. It consists of a first inner diameter protrusion 53 provided therein and a second inner diameter protrusion 55 protruded from the other end in the axial direction. In the following description regarding the seal ring 50, "axial direction" means the axial direction of the seal ring unless otherwise specified.

In addition, the

protrusions

53, 55, and 57 protruding from the inner diameter surface 51a and the outer diameter surface 51b of the base 51 all extend radially outward from the inner circumferential surface and the outer circumferential surface of the base 51. , it has an annular shape that continues in the circumferential direction, that is, it is an annular protrusion that is not interrupted midway in the circumferential direction of the base portion 51 .

The first inner diameter side protrusion 53 has a top portion 53a that most protrudes from the inner diameter surface 51a of the base portion 51, an outer surface 53b located on the outer side in the axial direction, and an inner surface 53c located on the inner side in the axial direction. There is. The inner surface 53c is a surface facing the second inner diameter protrusion 55 adjacent to the axial direction, and the outer surface 53b is opposite to the surface facing the second inner diameter protrusion 55 (inner surface 53c). It is on the side.

Further, the second inner diameter protrusion 55 has a top portion 55a that most protrudes from the inner diameter surface 51a of the base portion 51, an outer surface 55b located on the outer side in the axial direction, and an inner surface 55c located on the inner side in the axial direction. are doing. The inner surface 55c is a surface facing the first inner diameter protrusion 53 adjacent to the axial direction, and the outer surface 55b is opposite to the surface facing the first inner diameter protrusion 53 (inner surface 55c). It is on the side.

Further, among the inner diameter side protrusions, the outer surface 55b of the inner diameter side protrusion (second inner diameter side protrusion 55) located closest to the return direction F2 side opposite to the damper braking direction F1 is the inner diameter surface of the base portion 51. As it moves away from 51a, it has a shape that inclines toward the other axially adjacent inner diameter side protrusions.

Specifically, among the two inner

diameter side protrusions

53 and 55, the outer surface 55b of the second inner diameter side protrusion 55, which is located closest to the damper return direction F2, moves away from the inner diameter surface 51a of the base 51. It forms an inclined surface inclined toward the first inner diameter side protrusion 53 adjacent in the axial direction. In the case of this embodiment, as the outer surface 53b of the first inner diameter side protrusion 53 located on the damper braking direction F1 side also moves away from the inner diameter surface 51a of the base 51, the second inner diameter side protrusion adjacent in the axial direction It forms an inclined surface that slopes toward the portion 55.

Furthermore, the outer surface 53b of the first inner diameter side protrusion 53 is a continuous surface (flush) with no step with respect to one end surface 51c of the base 51 in the axial direction, and similarly, the outer surface 53b of the first inner diameter side protrusion 53 is a continuous surface (flush) with no step. The outer surface 55b of the protrusion 55 is also continuous with the other end surface 51d of the base 51 in the axial direction without any step.

Further, the

top portions

53a and 55a of the inner

diameter side protrusions

53 and 55 have rounded shapes, respectively, so as to form arcuate curved surfaces. Further, the inner surface 53c of the first inner diameter protrusion 53 and the inner surface 55c of the second inner diameter protrusion 55 are arranged so that they are substantially parallel to each other (substantially perpendicular to the axial direction of the seal ring 50). ), are placed opposite each other. Note that the first inner diameter side protrusion 53 and the second inner diameter side protrusion 55 have a shape that is line symmetrical with respect to the axial center line S (described later) of the seal ring 50, and the inner diameter side protrusion 51a of the base portion 51 The protrusion height from the top is also the same.

In summary, the

inner diameter protrusions

53 and 55 in this embodiment generally have one side substantially perpendicular and the other side gradually becoming wider from the tops 53a and 55a toward the inner diameter surface 51a of the base 51. It has a cross-sectional shape in the shape of a right triangular mountain.

Also, the boundary portion (corner portion) between the inner surface 53c of the first inner diameter side protrusion 53 and the inner diameter surface 51a of the base 51, and the inner surface 55c of the second inner diameter side protrusion 55 and the inner diameter surface of the base 51. R-shaped

fillet portions

53d and 55d are formed at the boundary portions (corner portions) with 51a, respectively.

On the other hand, the outer diameter side protrusion 57 is the outer diameter surface 51b of the base 51, and protrudes from the center position in the axial direction. It has an outer surface 57b located at one end and an outer surface 57c located at the other end in the axial direction.

Further, the top portion 57a of the outer diameter side protrusion 57 has a rounded shape to form an arcuate curved surface. The top portion 57a of the outer diameter protrusion 57 is always in contact with the inner circumferential surface of the cylinder 20 and is in pressure contact with the inner circumferential surface of the cylinder 20. Note that the above-mentioned "always" means that the piston 40 is in the cylinder 20 when the piston 40 is stationary, when the piston 40 moves in the damper braking direction F1, and when the piston 40 moves in the damper return direction F2. It means all possible states (the same applies in the following explanation).

Furthermore, both

outer surfaces

57b and 57c of the outer diameter protrusion 57 form inclined surfaces that gradually make the outer diameter protrusion 57 wider as they approach the outer diameter surface 51b of the base 51. That is, the outer diameter side protrusion 57 has a cross-sectional shape that gradually becomes wider from the apex 57a toward the outer diameter surface 51b of the base 51, and has a substantially equilateral triangular mountain shape (which can also be called a widening shape). ing. Note that both outer side surfaces 57b and 57c of the outer diameter side protrusion 57 are inclined so as to be line symmetrical with respect to the axial center line S of the seal ring 50.

Furthermore, R-shaped

fillet portions

57d and 57d are formed at the boundary portions (corner portions) between both outer side surfaces 57b and 57c of the outer diameter side protrusion 57 and the outer diameter surface 51b of the base portion 51, respectively. ing.

The entirety of the seal ring 50 described above has the following characteristics with respect to the axial center line S passing through the axial center (a line perpendicular to the axial direction of the seal ring 50 and passing through the top 57a of the outer diameter side protrusion 57). It has a line-symmetrical cross-sectional shape (see FIG. 5). Further, each part constituting the seal ring 50, that is, the base portion 51, the inner

diameter side protrusions

53, 55, and the outer diameter side protrusion 57 are all integrally formed.

In this seal ring 50, at least one of the

inner protrusions

53 and 55 is in contact with the bottom surface 45a of the annular groove 45, and the outer protrusion 57 is in contact with the outer diameter surface 51b of the base 51. The outer protrusion 57 has an annularly protruding structure such that the apex 57a of the outer protrusion 57 is disposed at a corresponding position between the

apexes

53a and 55a of the

inner protrusions

53 and 55 adjacent in the axial direction. It has become. In other words, the top 57a of the outer protrusion 57 does not overlap in the axial direction of the seal ring 50, but is shifted from the top 53a, 55a of the

inner protrusion

53, 55. It is set up like this.

Further, the outer diameter side protrusion 57 has an outer diameter side protrusion at a position corresponding to the middle between the tops 53a and 55a of the two inner diameter side protrusions 53 and 55 (a position between the top 53a and the top 55a). The top portion 57a of the portion 57 is disposed.

Further, the

inner surfaces

53c and 55c of the axially adjacent inner

diameter side protrusions

53 and 55 are located on the outer side in the axial direction than the top 57a of the outer diameter side protrusion 57. The width W2 between the

outer surfaces

57b and 57c is smaller than the distance W3 between the tops 53a and 55a of the axially adjacent

inner projections

53 and 55.

Note that the width W2 between the

outer surfaces

57b and 57c of the outer diameter side protrusion 57 is defined as the width W2 from the point P1 where the fillet 57d continuous from the base end of the outer surface 57b and the outer diameter surface 51b of the base 51 intersect, It means the length up to a point P2 where the fillet portion 57d continuous to the outer surface 57c and the outer diameter surface 51b of the base portion 51 intersect. That is, the width of the outer diameter side protrusion 57 is a concept that includes the widened portions of the

fillets

57d, 57d that are connected to both the outer side surfaces 57b, 57c.

Further, when the piston 40 is inserted into the cylinder 20 with the seal ring 50 attached to the annular groove 45, the outer surface of the seal ring 50 with the

inner diameter protrusions

53 and 55 in contact with the bottom surface 45a of the annular groove 45 The radial protrusion 57 is pressed against the inner circumferential surface of the cylinder 20, so that the seal ring 50 is bent and deformed as shown in FIGS. 7 and 8.

In the case of this embodiment, as described above, the piston 40 is inserted into the cylinder 20, and the outer diameter side protrusion 57 that is in pressure contact with the inner peripheral surface of the cylinder 20 is pressed against the inner peripheral surface of the cylinder 20. , both

side portions

51e, 51e of the outer diameter side protrusion 57 of the base portion 51 are bent and deformed so as to curve slightly inward in the radial direction of the seal ring 50 (see FIG. 7), and accordingly, the inner diameter side protrusion The

portions

53 and 55 are flexibly deformed so as to expand toward both ends of the seal ring 50 in the axial direction. That is, the

outer surfaces

53b, 55b of the inner

diameter side protrusions

53, 55 are deformed so as to approach the inner surface of the annular groove 45 (the

inner surfaces

41a, 42a of each side wall portion 41, 42), and the inner diameter side protrusions By deforming the

inner surfaces

53c and 55c of the

portions

53 and 55 so as to spread out from each other, the pair of inner

diameter side protrusions

53 and 55 are deflected and deformed so as to spread toward both ends of the seal ring 50 in the axial direction.

Furthermore, in this embodiment, the protrusion height of the outer diameter side protrusion 57 from the outer diameter surface 51b of the base portion 51 in the free state of the seal ring 50 before the seal ring 50 is installed in the annular groove 45 is (The length between the top 57a of the outer diameter side protrusion 57 and the outer diameter surface 51b of the base 51) is H, and when the seal ring is free, the tops 53a, 55a of the inner

diameter side protrusions

53, 55 and the outer diameter side Let L1 be the length in the radial direction between the top 57a of the protrusion 57 and L2 be the length between the inner circumferential surface of the cylinder 20 and the bottom surface 45a of the annular groove 45, which the

inner protrusions

53 and 55 abut. When this happens, the setting is such that H>L1-L2.

Furthermore, in the case of this embodiment, as shown in FIG. 55 and the wrap amount R2 is set as follows.

That is, as shown in FIG. 5, the top 57a of the outer diameter side protrusion 57 in the seal ring free state and the outer diameter side protrusion 57 in pressure contact with the inner peripheral surface of the cylinder when the seal ring 50 is attached to the annular groove 45. The displacement amount with respect to the top portion 57a (see the two-dot chain line in FIG. 5) is defined as the wrap amount R1 of the outer diameter side protrusion 57 with respect to the inner circumferential surface of the cylinder 20. Furthermore, the

top portions

53a, 55a of the inner

diameter side protrusions

53, 55 in the seal ring free state, and the

top portions

53a, 53a of the inner

diameter side protrusions

53, 55 that contact the bottom surface of the annular groove when the seal ring 50 is attached to the

annular groove

45, 55a (see the two-dot chain line in FIG. 5) is defined as the overlap amount R2 of the inner

diameter side protrusions

53, 55 with respect to the bottom surface 45a of the annular groove 45. In this case, the setting is such that H>R1+R2.

Next, the operation of the seal ring 50 within the annular groove 45 when the piston 40 moves in the damper braking direction F1 and when the piston 40 moves in the damper return direction F2 will be described.

When the piston 40 is stationary, the seal ring 50 has the top 57a of the outer protrusion 57 in pressure contact with the inner circumferential surface of the cylinder 20, and the tops 53a and 55a of the

inner protrusion

53 and 55 in the annular groove. A seal ring 50 is disposed within the annular groove 45 so as to be in contact with the bottom surface 45 a of the seal ring 45 . In this case, as shown in FIGS. 7 and 8, the seal ring 50 is disposed within the cylinder 20 in a deformed state from the seal ring free state shown in FIG.

When the piston 40 moves in the damper braking direction F1 from this state, a frictional force opposite to the damper braking direction F1 acts on the outer diameter side protrusion 57 from the inner peripheral surface of the cylinder 20. The seal ring 50 is pushed toward the damper return direction F2. As a result, as shown in FIG. 7, the other axial end surface 51d of the base 51 of the seal ring 50 comes into contact with the inner surface (the inner surface 42a of the second side wall portion 42) on the other axial end side of the annular groove 45. Then, the gap between the inner surface of the annular groove 45 on the other axial end side and the other end surface 51d of the base 51 is sealed, and the gap between the inner circumferential surface of the cylinder 20 and the outer circumferential surface of the seal ring 50 is also sealed. Since the openings of the pair of notched

grooves

48, 48 on the second side wall portion 42 side are respectively closed, the first chamber V1 in the cylinder 20 is depressurized and damper braking force is exerted.

On the other hand, when the piston 40 moves in the damper return direction F2, a frictional force in the opposite direction to the damper return direction F2 acts on the outer diameter side protrusion 57 from the inner peripheral surface of the cylinder 20. 50 is pushed toward the damper braking direction F1. As a result, as shown in FIG. 8, one axial end surface 51c of the base 51 of the seal ring 50 comes into contact with the inner surface (the inner surface 41a of the first side wall 41) on the one axial end side of the annular groove 45. The other axial end surface 51d of the base portion 51 is separated from the inner surface on the other end side of the annular groove 45 (the inner surface 42a of the second side wall portion 42). Then, the opening of each notch groove 48 on the second side wall portion 42 side opens, so that the air in the first chamber V1 in the cylinder 20 passes through each notch groove 48, as shown by the arrow in FIG. Then, it flows out into the second chamber V2. As a result, the damper braking force is released.

(Modified example)
The shapes and structures of the cylinder, rod, piston, seal ring, etc. that constitute the damper device in the present invention are not limited to the above embodiments.

Although the wall portion 21 of the cylinder 20 in this embodiment has a substantially thin cylindrical shape, the wall portion of the cylinder may have a substantially rectangular tube shape or a substantially cylindrical shape, for example. In this case, it is preferable that the rod, piston, seal ring, seal cap, detachment prevention cap, etc. also have a shape that corresponds to the wall of the cylinder.

Further, the cylinder 20 of this embodiment is closed with an end wall 25 disposed at the other end in the axial direction, but for example, a through hole is formed in the end wall disposed at the other end of the cylinder. It is also possible to form a structure in which the through hole is opened and closed by a seal cap.

Further, the rod 30 of this embodiment has a prismatic shaft portion 31, but the rod may include, for example, a shaft portion and a pair of side walls disposed on both sides of the shaft portion via a plurality of ribs. It may have a structure consisting of a long plate-like or cylindrical shaft, as long as pistons can be connected in series.

Further, the annular groove 45 in the piston 40 of this embodiment has a bottom surface 45a that is parallel to the axial direction of the piston 40, but the annular groove may have an inclined bottom surface or a stepped shape. It may be done without.

Furthermore, the seal ring 50 of this embodiment has two inner

diameter side protrusions

53 and 55, which are provided so as to protrude from both axial ends of the inner diameter surface 51a. There may be three or more protrusions on the inner diameter side. Further, in the case of this embodiment, both of the inner

diameter side protrusions

53 and 55 come into contact with the bottom surface 45a of the annular groove 45, but at least one inner diameter side protrusion comes into contact with the bottom surface of the annular groove. Just make contact.

Further, the

outer surfaces

53b, 55b of the inner

diameter side protrusions

53, 55 are flush with the

axial end surfaces

51c, 51d of the base 51 without any step. The outer surface may be arranged axially inward with respect to both axial end surfaces of the base (may be provided with a step).

Furthermore, although the

inner surfaces

53c and 55c of the

inner diameter protrusions

53 and 55 are parallel to each other, one or both inner surfaces may be inclined with respect to the axial direction of the piston. Furthermore, the outer surfaces of the inner diameter protrusions may be perpendicular to the axial direction of the piston, or may be inclined in directions away from each other.

Further, both

outer surfaces

57b and 57c of the outer diameter side protrusion 57 are inclined so as to be line symmetrical with respect to the axial center line S of the seal ring 50. The side surfaces may have different inclination angles relative to the axial direction of the seal ring, or may be perpendicular to the axial direction of the piston.

Furthermore, in this embodiment, when the piston 40 moves in a direction away from the end wall 25 of the cylinder 20 (when the piston 40 moves in the damper braking direction F1), the braking force due to the reduced pressure in the first chamber V1 is reduced. is applied and the piston 40 moves in a direction approaching the end wall 25 of the cylinder 20 (when the piston 40 moves in the damper return direction F2), the braking force is released. . However, on the contrary, when the piston 40 moves in the direction approaching the end wall 25 of the cylinder 20, the damper braking force acts, and the piston 40 moves in the direction away from the end wall 25 of the cylinder 20. The damper braking force may be released when the vehicle moves.

Furthermore, in this embodiment, one member is used as a fixed body such as an instrument panel accommodating part, and the other member is used as an opening/closing body such as a glove box or a lid, but the pair of members can be moved close to and separated from each other. There is no particular limitation as long as it is.

Furthermore, in this embodiment, an air chamber (first chamber V1) is formed in the cylinder 20 on the side in the insertion direction of the rod 30 from the seal ring 50, but on the opposite side of the rod insertion direction in the cylinder. An air chamber may be provided on the side. For example, an exhaust hole is formed in the end wall of the cylinder, and a seal cap that allows the exhaust hole to be opened and closed is attached to the periphery of the exhaust hole. Furthermore, the cap attached to the opening at one end of the cylinder has a structure that can seal the periphery of the opening and also seal the gap between the rod insertion port and the rod inserted into the rod insertion port. As such, a sealed air chamber is provided inside the cylinder on the opposite side of the rod insertion direction. Then, when the piston moves away from the end wall of the cylinder (when it moves in the opposite direction to the direction in which the rod is inserted), the air chamber is pressurized, so that damper braking force is exerted. It has become. Note that when the piston moves close to the end wall of the cylinder (moves in the rod insertion direction), the seal cap opens the exhaust hole, the air in the air chamber is exhausted, and the damper braking force is released. be done.

(effect)
Next, the effects of the damper device 10 having the above configuration will be explained.

In this damper device 10, the piston 40 is stationary within the cylinder 20 when one member (fixed body, etc.) and the other member (opening/closing body, etc.) are close to each other. In this state, the top 57a of the outer protrusion 57 is in contact with the inner peripheral surface of the cylinder 20, and the tops 53a, 55a of the

inner protrusions

53, 55 are in contact with the bottom 45a of the annular groove 45. A seal ring 50 is disposed within the annular groove 45.

From the above state, when one member moves in a direction away from the other member (when the opening/closing body opens from the fixed body), the piston 40 moves within the cylinder 20 in the damper braking direction F1, and The rod 30 is pulled out from the opening 23 side of the cylinder 20. Then, as explained in paragraph 0059 above, the pressure in the first chamber V1 in the cylinder 20 is reduced, so a damper braking force is applied to the piston 40, causing one member to slowly move relative to the other member. (the opening/closing body can be opened slowly from the fixed body).

Furthermore, when one member moves in a direction closer to the other member (when closing the opening/closing body with respect to the fixed body), the piston 40 moves within the cylinder 20 in the damper return direction F2, and The rod 30 is pushed into the cylinder 20.

Then, a frictional force opposite to the damper return direction F2 acts on the outer diameter protrusion 57 from the inner circumferential surface of the cylinder 20, so the seal ring 50 is pushed in the damper braking direction F1 by the frictional force. As explained in paragraph 0060 above, the opening of each notch groove 48 on the second side wall portion 42 side opens, and the air in the first chamber V1 passes through each notch groove 48 to the second chamber V2. and the damper braking force is released.

When the piston 40 is inserted into the cylinder 20 with the seal ring 50 attached to the annular groove 45, the outer diameter protrusion 57 that is in pressure contact with the inner circumferential surface of the cylinder 20 is pressed against the inner circumferential surface of the cylinder 20. However, at the same time, a reaction force F3 against the pressing force acts on the inner circumferential surface of the cylinder 20 via the outer diameter side protrusion 57.

At this time, in this damper device 10, at least one of the

inner protrusions

53 and 55 contacts the bottom surface 45a of the annular groove 45, and the outer protrusion 57 contacts the outer diameter surface 51b of the base 51. The structure protrudes annularly so that the apex 57a of the outer protrusion 57 is disposed at a corresponding position between the

apexes

53a and 55a of the

inner protrusions

53 and 55 adjacent in the axial direction. It becomes.

Therefore, since the seal ring 50 is easily bent and deformed, the reaction force F3 from the seal ring 50 acting on the inner peripheral surface of the cylinder 20 can be suppressed. In other words, the outer diameter side protrusion 57 is arranged so that its apex 57a is shifted from the apex 53a, 55a of the inner

diameter side protrusion

53, 55 without overlapping in the axial direction of the seal ring 50. Since the thickness of the seal ring 50 in the radial direction can be reduced, the base portion 51 can be easily bent and deformed, and the reaction force F3 acting on the inner peripheral surface of the cylinder 20 can be suppressed. be able to. As a result, the operating force of the piston 40 when the piston 40 moves in the damper return direction F2 can be reduced.

Moreover, the at least two inner

diameter side protrusions

53 and 55 make it easier to maintain the seal ring 50 in a stable posture, and when the piston 40 moves in the damper braking direction F1, the inner peripheral surface of the cylinder 20 and the seal ring 50 can be firmly sealed, and the desired damper braking force can be reliably exerted.

Further, in this embodiment, the inner

diameter side protrusions

53 and 55 are two pieces that respectively protrude from both ends of the base 51 in the axial direction, and the outer diameter side protrusion 57 is composed of two inner diameter side protrusions. The top 57a of the outer diameter side projection 57 is arranged at a position corresponding to the middle between the tops 53a and 55a of the side projections 53 and 55 (a position between the top 53a and the top 55a). There is.

According to the above aspect, since the inner

diameter side protrusions

53, 55 and the outer diameter side protrusion 57 have the above structure, the entire seal ring 50 has a shape that is line symmetrical with respect to the axial center line S. It can be made easier. As a result, when the seal ring 50 is attached to the annular groove 45, there is no directionality in the seal ring 50, so that the workability of attaching the seal ring 50 to the annular groove 45 can be improved. Further, the seal ring 50 attached to the annular groove 45 can be easily held in a more stable posture.

Furthermore, in this embodiment, the

inner surfaces

53c, 55c of the axially adjacent inner

diameter side protrusions

53, 55 are located axially outer than the top 57a of the outer diameter side protrusion 57, and The width W2 between the

outer surfaces

57b and 57c of the radial projection 57 is smaller than the distance W3 between the tops 53a and 55a of the axially adjacent inner

radial projections

53 and 55.

According to the above aspect, it becomes easier to ensure a wide gap between the axially adjacent inner diameter side protrusions 53 and 55 (the axial gap of the seal ring 50), so it becomes easier to bend and deform the base 51. , the operating force of the piston 40 when the piston 40 moves in the damper return direction F2 can be further reduced.

Furthermore, in this embodiment, the protrusion height of the outer diameter side protrusion 57 from the outer diameter surface 51b of the base portion 51 in the free state of the seal ring 50 before the seal ring 50 is installed in the annular groove 45 is (The length between the top 57a of the outer diameter side protrusion 57 and the outer diameter surface 51b of the base 51) is H, and the tops 53a, 55a of the inner

diameter side protrusions

53, 55 and the outer diameter side protrusion in the free state are The length in the radial direction between the top portion 57a of the portion 57 is L1, and the length between the inner circumferential surface of the cylinder 20 and the bottom surface 45a of the annular groove 45, which the

inner diameter protrusions

53, 55 abut, is L2. At this time, it is set so that H>L1-L2.

According to the above aspect, when the piston 40 is inserted into the cylinder 20 with the seal ring 50 attached to the annular groove 45, the outer diameter side surface (outer diameter surface 51b) of the base portion 51 is attached to the cylinder 20. can be prevented from coming into contact with the inner circumferential surface of the damper, and the operating force of the piston 40 when the piston 40 moves in the damper return direction F2 can be further reduced.

Furthermore, in this embodiment, among the inner diameter side protrusions, the outer surface 55b of the inner diameter side protrusion (second inner diameter side protrusion 55) located closest to the return direction F2 side opposite to the damper braking direction F1, The base portion 51 has a shape that inclines toward the other axially adjacent inner diameter side protrusions as the base portion 51 moves away from the inner diameter surface 51a.

According to the above aspect, when the seal ring 50 is attached to the annular groove 45, it is possible to prevent the second inner diameter side protrusion 55 from expanding beyond the other end surface 51d in the axial direction of the base 51. The sealing performance between the inner surface of the groove 45 located in the damper return direction F2 (the inner surface 42a of the second side wall portion 42) and the seal ring 50 can be improved. As a result, when the piston 40 moves in the damper braking direction F1, a desired damper braking force can be reliably exerted.

Further, in this embodiment, both

outer surfaces

57b and 57c of the outer diameter side protrusion 57 form inclined surfaces that make the outer diameter side protrusion 57 gradually wider as it approaches the outer diameter surface 51b of the base 51. ing.

According to the above aspect, since the outer diameter side protrusion 57 has a so-called flared shape, when the piston 40 moves in the damper braking direction F1, the frictional force from the inner peripheral surface of the cylinder 20 is applied to the outer diameter side protrusion. 57, the outer diameter side protrusion 57 can be made less likely to fall down (or be less likely to deform). As a result, it becomes easier to maintain the sealing performance of the outer diameter side protrusion 57 with respect to the inner circumferential surface of the cylinder 20, so that the damper braking force can be stably exerted.

Furthermore, the present invention is not limited to the embodiments described above, and various modified embodiments are possible within the scope of the gist of the present invention, and such embodiments are also included within the scope of the present invention. .

10 Damper device 20 Cylinder 23 Opening 30 Rod 40 Piston 45 Annular groove 45a Bottom surface 50 Seal ring 51 Base 53 First inner diameter protrusion 53a Top

53b Outer surface

53c Inner surface 55 Second inner diameter protrusion 55a Top

55b Outer surface

55c Inner surface 57 Outer diameter protrusion 57a

Top portions

57b, 57c Outer surface 60 Prevention cap

Claims

A damper device that is installed between a pair of members that move closer to each other and applies a braking force when the pair of members move closer to each other or move away from each other,
a cylinder with an opening at one end;
a rod movably inserted into the cylinder through the opening;
a piston connected to the rod and having an annular groove formed on its outer periphery;
a seal ring installed in the annular groove and pressed against the inner circumferential surface of the cylinder;
The seal ring is
a base having an annular shape and disposed within the annular groove;
at least two protrusions on the inner diameter side protruding from the inner diameter side surface of the base;
and an outer diameter protrusion that protrudes from the outer diameter side surface of the base and comes into contact with the inner peripheral surface of the cylinder,
At least one of the inner diameter protrusions abuts the bottom surface of the annular groove,
The outer diameter side protrusion is a surface on the outer diameter side of the base, and the top of the outer diameter side protrusion is located at a position corresponding to between the tops of the inner diameter side protrusions adjacent to each other in the axial direction. A damper device characterized in that it projects in an annular manner so as to be arranged.
The inner diameter side protrusions are composed of two protrusions respectively protruding from both ends of the base in the axial direction,
2. The outer diameter side protrusion is provided such that the top of the outer diameter side protrusion is located at a position corresponding to the middle of the tops of the two inner diameter side protrusions. damper device.
The inner surface of the inner diameter side protrusion adjacent to each other in the axial direction is located on the outer side in the axial direction than the top of the outer diameter side protrusion,
3. The damper device according to claim 1, wherein a width between both outer surfaces of the outer diameter side protrusion is smaller than an interval between the tops of the inner diameter side protrusions adjacent in the axial direction.
H is the protrusion height of the outer diameter side protrusion from the outer diameter side surface of the base in a free state of the seal ring before the seal ring is installed in the annular groove;
In the free state, the length in the radial direction of the top of the inner diameter side protrusion and the top of the outer diameter side protrusion is L1,
When L2 is the length of the inner circumferential surface of the cylinder and the bottom surface of the annular groove that the inner diameter side protrusion comes into contact with,
The damper device according to any one of claims 1 to 3, wherein the damper device is set so that H>L1-L2.
Among the inner diameter side protrusions, the outer surface of the inner diameter side protrusion located closest to the return direction opposite to the damper braking direction becomes adjacent to the inner diameter side surface in the axial direction as it moves away from the inner diameter side surface of the base. The damper device according to any one of claims 1 to 4, wherein the damper device is inclined toward the other inner diameter side protrusion.
Any one of claims 1 to 5, wherein both outer surfaces of the outer diameter side protrusion form inclined surfaces that gradually widen the outer diameter side protrusion as it approaches the outer diameter side surface of the base. 1. The damper device according to item 1.