JP2023034896A - damper - Google Patents

Abstract

To provide a damper where the brake force and the load when returned are easily adjusted by allowing easy change of the contact area of a friction member with respect to the inner peripheral face of a cylinder.SOLUTION: A damper 10 includes a cylinder 20, a piston 40 having a shaft part 50, and a friction member 70, the friction member 70 having an intermediate part 80 and a plurality of friction parts 90, the friction parts 90 each having a first inclined portion 91 and a second inclined portion 95 in slide contact with the inner peripheral face of the cylinder, the piston 40 having a pressing protruded part 57. When the first inclined portion 91 is pressed by the pressing protruded part 57, the second inclined portion 95 is expanded to be pressed against the inner peripheral face of the cylinder. As the pressing load is higher, the contact area with the inner peripheral face of the cylinder is larger, and as the pressing load is lower, the contact area with the inner peripheral face of the cylinder is smaller.SELECTED DRAWING: Figure 6

Description

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a damper used for braking, for example, opening and closing operations of a glove box of an automobile.

For example, a damper is sometimes used in a glove compartment of an automobile to suppress sudden opening of the lid and allow the lid to open gently.

As such a damper, Patent Document 1 below discloses an air damper having a cylinder, a piston that moves in the axial direction within the cylinder, a piston rod that moves the piston, and an elastic member (elastic packing) that contacts the piston. is described.

The elastic packing has a substantially annular shape having a peripheral wall continuous in the circumferential direction, the outer periphery of which forms a second engaging surface, and the inner periphery of the peripheral wall forming a first engaging surface with a mortar-shaped inclined surface. face is provided. Further, the outer peripheral surface of the piston has a conical inclined surface.

When the piston moves in one direction, the conical inclined surface engages with the mortar-shaped first engaging surface on the inner circumference of the elastic packing, and the second engaging surface on the outer circumference of the elastic packing moves into the cylinder. The degree of contact with the wall surface is increased.

JP 2019-086124 A

In the case of the air damper disclosed in Patent Document 1, the elastic packing has a substantially annular shape with a peripheral wall that is continuous in the circumferential direction, so that the cone-shaped first engaging surface is pushed by the conical inclined surface of the piston. However, it is difficult to deform the elastic packing, and it is difficult to adjust the degree of contact of the second engaging surface of the outer circumference of the elastic packing with the inner wall surface of the cylinder.

SUMMARY OF THE INVENTION Accordingly, it is an object of the present invention to provide a damper in which the contact area of the friction member with respect to the inner peripheral surface of the cylinder can be easily changed to facilitate adjustment of the damper's braking force and return load.

In order to achieve the above object, the present invention provides a damper that is attached between a pair of members that approach and separate from each other and that applies a braking force when the pair of members approach or separate, the damper having an opening at the end. , a piston having a shaft portion extending with a predetermined length and slidably inserted into the cylinder, and a friction member attached to the piston, wherein the friction member is an intermediate portion mounted on the outer periphery of the shaft portion while being spaced apart from the inner peripheral surface of the cylinder; and a plurality of friction portions that are in sliding contact with the inner peripheral surface of the cylinder, and each friction portion extends obliquely from the intermediate portion toward the return direction opposite to the damper braking direction of the piston. and a second inclined portion extending from the first inclined portion so as to incline in a damper braking direction of the piston and slidingly contacting the inner peripheral surface of the cylinder. a projection that contacts and presses the first inclined portion when sliding in the damper braking direction and separates from the first inclined portion when sliding in the return direction; The slanted portion is configured to be pushed and spread through the first slanted portion so as to be in pressure contact with the inner peripheral surface of the cylinder when the first slanted portion is pressed by the protrusion, and the When the pressing load from the protrusion to the first inclined portion is large, the contact area with the inner peripheral surface of the cylinder increases, and when the pressing load is small, the contact area with the inner peripheral surface of the cylinder increases. characterized by decreasing

According to the present invention, the intermediate portion of the friction member is spaced from the inner peripheral surface of the cylinder, and the plurality of friction portions are divided into a plurality of locations in the circumferential direction of the cylinder via the intermediate portion. Since it is arranged, each friction portion can be easily deformed. Therefore, it is possible to obtain a damper in which the braking force of the damper and the load at the time of return can be easily adjusted.

1 is an exploded perspective view showing one embodiment of a damper according to the present invention; FIG. It is a perspective view of the same damper. The piston which comprises the same damper is shown, (a) is the perspective view, (b) is the principal part expansion perspective view seen from the direction different from (a). FIG. 2 shows a friction member constituting the same damper, (a) being an enlarged perspective view thereof, and (b) being an enlarged perspective view when viewed from a direction different from (a). FIG. 2 is an enlarged perspective view of a principal part of the damper with a friction member attached to a piston; FIG. 4 is a cross-sectional view of the damper in a state where the head of the piston is close to the end wall of the cylinder; Fig. 3 is an enlarged cross-sectional perspective view of the main part of the damper; FIG. 3 is a cross-sectional view taken along the line AA of FIG. 2; In the same damper, it is a cross-sectional view of a state in which the head of the piston is separated from the end wall of the cylinder. In the same damper, the relationship between the friction member and the protrusion of the piston is shown, (a) is an explanatory view of the state where the protrusion is separated from the first inclined portion of the friction member, is in contact with the first inclined portion of the friction member, and (c) is an explanatory view of the state in which the projection is in contact with the first inclined portion of the friction member with a load smaller than that in (b). be. Fig. 10 shows another embodiment of a damper according to the present invention, where (a) is an explanatory view of a state in which the projection abuts against the first inclined portion of the friction member under a large load; ) is an explanatory view of a state in which the projection abuts on the first inclined portion of the friction member with a load smaller than the load.

(One embodiment of damper)
An embodiment of a damper according to the present invention will be described below with reference to the drawings.

As shown in FIGS. 1 and 2, the damper 10 is attached to a pair of members that are close to each other and separate from each other, and applies a braking force when both members come close to or separate from each other. It can be used for braking a glove box, a lid, or the like, which is openable and closable at the opening of the storage section provided in the management panel. In the following embodiments, one member is a fixed body such as an instrument panel accommodating portion, and the other member is a glove box, a lid, or the like attached to an opening of the fixed body so as to be openable and closable. Although described as an opening/closing body, the pair of members is not particularly limited as long as it can be moved toward and away from each other.

As shown in FIG. 1, the damper 10 of this embodiment includes a cylindrical cylinder 20 having an opening 25 at its end, a cap 30 attached to the opening 25 of the cylinder 20, a shaft 50 and a head. 60, mainly composed of a piston 40 slidably inserted into the cylinder 20, a seal ring 45 attached to the outer periphery of the head 60 of the piston 40, and a friction member 70 attached to the piston 40. there is

First, the cylinder 20 will be explained.

As shown in FIGS. 1 and 6, the cylinder 20 of this embodiment has a substantially cylindrical wall portion 21 that extends for a predetermined length, and an end portion on one end side in the axial direction (extending direction). A wall 23 is provided to block one end of the cylinder 20 .

In this embodiment, as shown in FIG. 8, the substantially cylindrical wall portion 21 has circular outer and inner peripheral surfaces when the cylinder 20 is viewed from the axial direction. The inner peripheral surface 21a has an arcuate shape extending along the circumferential direction of the wall portion 21 to form an arcuate shape. That is, the cylinder 20 of this embodiment has arcuate inner peripheral surfaces on at least two opposing locations of the inner peripheral surface 21a (here, the inner peripheral surface 21a of the wall portion 21 The entire circumference is an arc-shaped inner peripheral surface).

An opening 25 is provided on the other end side of the wall 21 in the axial direction, and a plurality of locking holes 25a are formed on the peripheral edge of the opening. Furthermore, a projecting piece 27 in the shape of a thin long plate protrudes from the outside of the wall portion 21, and mounting holes 27a are provided at both ends of the projecting piece 27, respectively. Via these mounting holes 27a, the cylinder 20 is fixed to one member (instrument panel, etc.) (not shown).

Next, the cap 30 will be explained.

The cap 30 of this embodiment has a substantially cylindrical insertion portion 31 inserted from the opening 25 of the cylinder 20, and a lid portion 33 connected to the base end side of the insertion portion 31. . A plurality of locking projections 31a are projected from the outer periphery of the insertion portion 31. As shown in FIG. The cap 30 is attached to the opening 25 of the cylinder 20 by engaging each locking projection 31a with the corresponding locking hole 25a of the cylinder 20 . This cap 30 prevents the piston 40 from falling out of the cylinder 20 .

Further, the lid portion 33 is formed with a long hole-shaped shaft portion insertion hole 33a at its radially central portion. Further, guide grooves 33b are formed on both sides of the shaft insertion hole 33a in the longitudinal direction and on both sides in the width direction (a total of four guide grooves 33b are formed).

Next, the piston 40 will be explained.

The piston 40 of this embodiment has a long plate-shaped shaft portion 50 extending over a predetermined length and is slidably inserted into the cylinder 20 . Further, the piston 40 of this embodiment has the above-described shaft portion 50 and a head portion 60 connected to the base end portion side of the shaft portion 50 in the axial direction (extending direction).

As shown in FIG. 5, the shaft portion 50 is inserted through a shaft portion insertion hole 85 (described later) of the intermediate portion 80 that constitutes the friction member 70, and as shown in FIG. 33a is inserted. A circular attachment hole 51 is formed at the tip of the shaft portion 50 in the axial direction. Through this mounting hole 51, the shaft portion 50 is fixed to the other member (not shown) (such as an opening/closing member).

Further, as shown in FIG. 1 , a pair of guide ridges 53 , 53 extending parallel to each other along the axial direction of the shaft portion 50 are provided on both side edges of the shaft portion 50 in the width direction. As shown in FIG. 8, the pair of guide ridges 53, 53 are provided on both side surfaces in the thickness direction of the shaft portion 50 (a total of four guide ridges 53 are provided). As shown in FIG. 1, each guide projection 53 has its longitudinal base end connected to a later-described pressing projection 57 of the piston 40 , and its longitudinal tip is connected to the mounting hole 51 . It extends all the way to the front. As shown in FIGS. 2 and 5, the guide ridges 53 are inserted into the corresponding guide grooves 33b of the cap 30 and the corresponding guide grooves 87 (described later) of the friction member 70, respectively. It serves as a slide guide when the piston 40 slides.

As shown in FIGS. 3(a) and 3(b), a support protrusion 55 is protrudingly provided at a position near the base end in the axial direction of the shaft portion 50 and at the central portion in the width direction of the shaft portion 50. ing. As shown in FIG. 8, the support projections 55 are a pair of projections provided on both sides of the shaft portion 50 in the thickness direction. As shown in FIG. 5, the support protrusion 55 engages with the front side peripheral edge of the shaft portion insertion hole 85 formed in the intermediate portion 80 of the friction member 70 to support the friction member 70 and the shaft portion 50. This restricts the positional displacement of the friction member 70 toward the distal end side in the axial direction. The support projection 55 also holds the friction member 70 on the outer circumference of the shaft portion 50 so that the friction member 70 is prevented from slipping out, together with the pressing projection 57 described below. The outer surface of the support protrusion 55 is formed with a tapered surface 55a whose protrusion amount gradually increases from the distal end side toward the proximal end side in the axial direction of the shaft portion 50. Workability is improved when the friction member 70 is attached.

In addition, at a position closer to the proximal end portion of the shaft portion 50 in the axial direction and further toward the proximal end side of the shaft portion 50 in the axial direction than the support protrusion 55 (the side closer to the head portion 60), a pressing force is provided. A protrusion 57 is provided. The pressing protrusion 57 has a flange shape extending annularly from the outer periphery of the shaft portion 50, and the outer peripheral surface thereof is circular.

As shown in FIGS. 5, 10(b) and 10(c), the pressing projection 57 pushes the friction portion 90 of the friction member 70 when the piston 40 slides in the damper braking direction indicated by the arrow F1 in FIG. 9 and 10(a), when the piston 40 slides in the return direction indicated by the arrow F2 in FIG. They are becoming separated from each other. Further, as shown in FIGS. 10(b) and 10(c), the pressing protrusion 57 presses the first inclined portion 91 and serves as a portion that spreads the second inclined portion 95 (this is due to frictional force). (described in detail in the description of the member 70). That is, this pressing protrusion 57 constitutes the "protrusion" in the present invention.

As shown in FIG. 10(a), outer peripheral edge portions 57a and 57b on the front side (the side away from the head 60) and the back side (the side close to the head 60) of the pressing projection 57 are rounded. ing. Since the outer peripheral edge portion 57a on the front side of the pressing projection 57 is rounded, damage to the first inclined portion 91 is prevented when the first inclined portion 91 of the friction portion 90 is pressed. there is

On the other hand, as shown in FIGS. 3(b) and 6, the head portion 60 includes a substantially disk-shaped base portion 61 and a substantially cylindrical shape extending slightly from the inner diameter side of the outer peripheral edge of the base portion 61. and a flange portion 63 annularly extending from the outer circumference of the distal end of the wall portion 62 in the direction in which the wall portion 62 extends.

An annular seal ring 45 made of an elastic material such as rubber or elastic elastomer is attached between the base portion 61 and the flange portion 63 on the outer circumference of the wall portion 62 . The seal ring 45 is in sliding contact with the inner peripheral surface 21a of the wall portion 21 of the cylinder 20. As shown in FIG. That is, the seal ring 45 constitutes the "seal portion" of the present invention. Also, the thickness of the seal ring 45 is smaller than the dimension of the gap between the base portion 61 and the flange portion 63 . As a result, the seal ring 45 is slidable in the axial direction of the piston 40 between the base portion 61 and the flange portion 63 .

As shown in FIGS. 6 and 9, a first chamber R1 is formed on the piston pushing direction side (see arrow F2 in FIG. 9) with the seal ring 45 (seal portion) as a boundary, and the piston pulling direction side (see arrow F2 in FIG. 9). A second chamber R2 communicating with the external space of the cylinder 20 is formed in the second chamber R2 (see arrow F1 in FIG. 6). In this embodiment, the first chamber R1 is formed on the end wall 23 side of the cylinder 20, and the second chamber R2 is formed on the opening 25 side of the cylinder 20. As shown in FIG.

Moreover, as shown in FIGS. 3A and 3B, a plurality of cutouts 64 are formed along the outer peripheral edge of the base 61 and the wall 62 . In this embodiment, as shown in FIG. 8, a total of eight cutouts 64 are formed in two locations on the head 60 facing each other in the radial direction, with four cutouts 64 each. Each notch 64 cuts the entire thickness direction of the outer peripheral edge of the base 61 , and is formed to extend slightly forward of the flange 63 of the wall 62 . As shown in FIG. 7, an air flow passage R3 is formed through the notch 64 so that the first chamber R1 and the second chamber R2 are communicated with each other.

Furthermore, as shown in FIG. 3(b), from the back surface of the base portion 61 of the head portion 60 (the surface close to the end wall 23 of the cylinder 20), a substantially C-shaped portion is formed by cutting out a portion of the cylindrical wall. The formed wall portions 66 and 67 protrude concentrically. As indicated by broken lines in FIG. 3, orifices 68 having a small diameter penetrate through the base portion 61 via recesses 68a at positions aligned with the cutout portions of the wall portions 66 and 67. formed (see FIG. 7).

In the damper 10, the head 60 of the piston 40 slides away from the end wall 23 of the cylinder 20 as indicated by arrow F1 in FIG. When slid in the braking direction, the seal ring 45 moves toward the flange portion 63 of the head portion 60 (see the phantom line in FIG. 7) and is displaced from the notch portion 64 . As a result, the gap between the outer periphery of the head 60 of the piston 40 and the inner peripheral surface 21a of the wall 21 of the cylinder 20 is closed by the seal ring 45, and air flows only through the orifice 68. In other words, the seal ring 45 closes the air flow passage R3 to block air flow between the first chamber R1 and the second chamber R2.

As a result, the pressure in the air chamber R1 of the cylinder 20 is reduced, so that the piston 40 is applied with a braking force. That is, a braking force is applied to the piston 40 by the air damper. By providing the orifice 68, air can flow between the first chamber R1 and the second chamber R2 even when the air flow passage R3 is closed, so that the braking force of the air damper can be adjusted. It's becoming

On the other hand, as indicated by arrow F2 in FIG. 9, the head 60 of the piston 40 slides in a direction closer to the end wall 23 of the cylinder 20, i. When slid in the opposite return direction (hereinafter also simply referred to as the “return direction”), the seal ring 45 moves toward the base 61 of the head 60 (see phantom lines in FIG. 7) and aligns with the notch 64. position. As a result, the airflow passage R3 is located inside the seal ring 45. As shown in FIG. In other words, the seal ring 45 opens the air flow path R3 to enable air flow between the first chamber R1 and the second chamber R2.

As a result, the air in the first chamber R1 of the cylinder 20 is smoothly exhausted to the second chamber R2 side through the air flow passage R3, so that the braking force of the air damper applied to the piston 40 is rapidly applied. is set to be released at

Thus, in this embodiment, the seal ring 45 that forms the seal closes the air flow passage R3 when the piston 40 slides in the damper braking direction, and closes the air flow passage R3 when it slides in the return direction. configured to open.

Note that each component of the piston 40 excluding the seal ring 45 (the shaft portion 50, the guide projection 53, the support projection 55, the pressing projection 57, the head portion 60, the base portion 61, the wall portion 62, the flange portion, etc.) 63, walls 66, 67, etc.) are all integrally formed.

Next, the friction member 70 attached to the piston 40 will be described with reference to FIGS. 4-10.

Like the seal ring 45, the friction member 70 is made of an elastic material such as rubber or elastic elastomer, and is mounted on the outer periphery of the shaft portion 50 while being spaced apart from the inner peripheral surface 21a of the cylinder 20. and a plurality of friction portions 90 arranged so as to be divided into a plurality of locations in the circumferential direction of the cylinder 20 via the intermediate portion 80 and in sliding contact with the inner peripheral surface 21a of the cylinder 20. ing.

As shown in FIGS. 3 and 4, the intermediate portion 80 has a long flat plate shape with a constant thickness and a length dimension smaller than the inner diameter of the cylinder 20 and extending a predetermined length. This intermediate portion 80 is thinner than the friction portion 90 . That is, as shown in FIG. 10(a), the intermediate portion 80 is formed with a thickness T1 that is smaller than the thickness T2 of the friction portion 90. As shown in FIG.

Arc-shaped outer peripheral surfaces 81 , 81 are provided at both ends of the intermediate portion 80 in the longitudinal direction. Furthermore, a pair of outer side surfaces 83, 83 parallel to each other are provided on both side portions in the width direction perpendicular to the longitudinal direction of the intermediate portion 80. As shown in FIG. That is, a pair of outer side surfaces 83 , 83 are formed by cutting parallel planes at two radially opposed portions of the outer periphery of the intermediate portion 80 . In a state in which the friction member 70 is arranged inside the cylinder 20, the pair of outer side surfaces 83, 83 of the intermediate portion 80 are separated from the inner peripheral surface 21a of the wall portion 21 of the cylinder 20. (See Figures 7 and 8). Therefore, a gap is formed between the outer surface 83 of the intermediate portion 80 and the inner peripheral surface 21a of the wall portion 21 of the cylinder 20, so that the air in the cylinder 20 can flow through this gap.

A shaft insertion hole 85 having an elongated hole shape is formed in the radially central portion of the intermediate portion 80 . Further, guide grooves 87 are formed on both sides of the shaft insertion hole 85 in the longitudinal direction and on both sides in the width direction (a total of four guide grooves 87 are formed). . As shown in FIG. 5, the shaft portion 50 of the piston 40 is inserted into the shaft portion insertion hole 85, and the corresponding guide ridges 53 of the shaft portion 50 of the piston 40 are inserted into the respective guide grooves 87. , the intermediate portion 80 is attached to the outer circumference of the shaft portion 50, and the friction member 70 is attached to the piston 40 by extension.

On the other hand, the friction portion 90 includes a first inclined portion 91 extending from the intermediate portion 80 in an inclined direction toward the return direction of the piston 40 and a and a second inclined portion 95 which extends obliquely and is in sliding contact with the inner peripheral surface 21a of the cylinder 20 .

More specifically, this embodiment has a pair of friction portions 90 , 90 extending from the arcuate outer peripheral surfaces 81 , 81 of the intermediate portion 80 . Each friction portion 90 includes a first inclined portion 91 extending obliquely outward from an arc-shaped outer peripheral surface 81 of the intermediate portion 80 toward the damper return direction (see arrow F2), and the first inclined portion 91 and a second inclined portion 95 that is folded back through a valley-shaped bent valley-shaped portion 93 located at the tip in the extending direction of the and extends obliquely outward in the damper braking direction (arrow F1). Become. That is, as shown in FIGS. 6 and 10(a), when the friction member 70 is viewed from the side (when viewed from a direction orthogonal to the outer surface 83 of the intermediate portion 80), the friction portion 90 has It has a substantially V shape formed by a first inclined portion 91 and a second inclined portion 95 .

Further, in this embodiment, since the pair of friction portions 90, 90 extend from the outer peripheral surfaces 81, 81 of the intermediate portion 80, the first inclined portions 91, 91 are separated from each other in the damper return direction. The second sloping portions 95, 95 are folded back from the tips of the first sloping portions 91, 91 via the trough portions 93, 93, and the damper It can also be said that they form a substantially inverted V-shape extending in the braking direction while being separated from each other and gradually expanding.

Further, the outer peripheral surface 96 of the second inclined portion 95 of each friction portion 90 has an arcuate shape that fits the arcuate inner peripheral surface 21a of the wall portion 21 of the cylinder 20 .

The second inclined portion 95 presses against the inner peripheral surface 21a of the cylinder 20 via the first inclined portion 91 when the first inclined portion 91 is pressed by the protrusion (the pressing protrusion 57). When the pressing load from the pressing protrusion 57 to the first inclined portion 91 is large, the contact area with the inner peripheral surface 21a of the cylinder 20 increases (Fig. 10(b) ), and when the pressing load is small, the contact area with the inner peripheral surface 21a of the cylinder 20 decreases (see FIG. 10(c)).

Specifically, the pressing load from the pressing protrusion 57 to the first inclined portion 91 changes depending on the speed at which the piston 40 slides in the cylinder 20 in the damper braking direction. For example, when the items stored in the glove box are heavy, the sliding speed of the piston 40 in the cylinder 20 toward the damper braking direction increases. , the sliding speed of the piston 40 in the cylinder 20 toward the damper braking direction is slowed down.

In this embodiment, when the piston 0 is pushed into the cylinder 20 in the direction in which the head 60 approaches the end wall 21 of the cylinder 20, as shown in FIG. The R-shaped outer peripheral edge portion 57a on the front side of the pressing protrusion 57 of the piston 40 is separated from the back surface 91a of the piston 91 (the surface facing the pressing protrusion 57 of the piston 40).

From the above state, when the piston 40 slides in the damper braking direction and the head 60 of the piston 40 slides away from the end wall 23 of the cylinder 20 as indicated by the arrow F1 in FIG. ) and (c), the outer peripheral edge portion 57a of the pressing protrusion 57 of the piston 40 contacts and presses the back surface 91a of the first inclined portion 91, and the 2 sloping portion 95 is spread.

At this time, when the pressing load of the pressing protrusion 57 is large, as shown in FIG. , and is pressed against the inner peripheral surface 21a of the cylinder 20. As shown in FIG. On the other hand, when the pressing load of the pressing protrusion 57 is lower than in the case of FIG. 10(b), as shown in FIG. Only a portion is pressed against the inner peripheral surface 21a of the cylinder 20 . Also, the pressure contact area of the second inclined portion 95 with respect to the inner peripheral surface 21a of the cylinder 20 shown in FIG. It is larger than the pressure contact area of the inclined portion 95 .

Thus, the contact area of the outer peripheral surface 96 of the second inclined portion 95 with respect to the inner peripheral surface 21a of the cylinder 20 varies depending on the magnitude of the pressing load from the pressing protrusion 57 of the piston 40 .

Further, as shown in FIG. 6, when the friction portions 90, 90 of the friction member 70 are not pressed by the pressing protrusion 57 of the piston 40, the ends of the pair of first inclined portions 91, 91 in the extension direction is formed to be larger than the outer diameter L2 of the pressing protrusion 57 of the piston 40 . Therefore, the pressing projection 57 of the piston 40 enters between the pair of first inclined portions 91, 91, and the pressing projection 57 can reliably press the back surfaces 91a, 91a of the first inclined portions 91, 91. It's becoming

Further, the maximum width dimension of the pair of second inclined portions 95, 95 (from the extending direction tip of the outer peripheral surface 96 of one second inclined portion 95 to the extending direction tip of the outer peripheral surface 96 of the other second inclined portion 95 ) is formed to be larger than the inner diameter dimension of the inner peripheral surface 21 a of the wall portion 21 of the cylinder 20 . Therefore, even when the friction member 70 is arranged in the cylinder 20 and the pair of first inclined portions 91, 91 is not pressed by the pressing protrusion 57 of the piston 40, the pair of second inclined portions 95, 95 is not pressed. The outer peripheral surfaces 96 , 96 of the cylinder 20 are pressed against the inner peripheral surface 21 a of the wall portion 21 of the cylinder 20 .

All of the components of the friction member 70 described above (the intermediate portion 80, the friction portion 90 including the first inclined portion 91 and the second inclined portion 95, etc.) are all integrally formed.

(Modification)
The shape and structure of the cylinder, the cap, the shaft portion and the head portion of the piston, and the intermediate portion and the friction portion of the friction member, which constitute the damper in the present invention, are not limited to the above embodiments.

The wall portion 21 of the cylinder 20 in this embodiment has a substantially cylindrical shape, but the wall portion of the cylinder may have, for example, a substantially square tubular shape or a thin box shape. In this case, it is preferable that the head portion and seal portion constituting the piston also have a shape corresponding to the wall portion of the cylinder.

In addition, the cylinder 20 of this embodiment is closed with an end wall 23 at one end in the axial direction. , these openings and through holes may be closed with a cap separate from the cylinder.

Furthermore, the seal portion in this embodiment is separate from the piston 40 and consists of a seal ring 45 that is attached to the head portion 60. However, for example, the seal portion may be provided integrally with the outer periphery of the head portion.

Also, the friction member 70 of this embodiment has a pair of friction portions 90 , 90 , but may have three or more friction portions. Any shape or structure may be used as long as it is arranged so as to be divided into a plurality of locations in the direction. In addition, the intermediate portion 80 has a pair of outer surfaces 83, 83 which are spaced apart from the inner peripheral surface 21a of the cylinder 20, but have only one straight cut surface in the intermediate portion. may be formed, or three or more cut surfaces may be formed.

Furthermore, in this embodiment, the second inclined portion 95 is spread through the first inclined portion 91 so that the second inclined portion 95 comes into pressure contact with the inner peripheral surface 21a of the cylinder 20. In addition to the second inclined portion, other portions may be pressed against the inner peripheral surface of the (this will be described in another embodiment).

Further, in this embodiment, when the head 60 of the piston 40 moves away from the end wall 23 of the cylinder 20, the braking force (braking force of the air damper) due to the pressure reduction in the first chamber R1 and the , and the braking force by the friction member 70 (the braking force by the friction damper) are applied to the piston 40, while the head 60 moves toward the end wall 23 of the cylinder 20. , the braking force by the air damper and the braking force by the friction damper are released.

However, on the contrary, when the head 60 of the piston 40 moves in the direction to approach the end wall 23 of the cylinder 20, the braking force by the air damper and the braking force by the friction damper are applied to the piston 40. On the other hand, when the head 60 of the piston 40 moves away from the end wall 23 of the cylinder 20, the braking force by the air damper and the braking force by the friction damper may be released. . In this case, the first inclined portion of the friction portion is inclined in the return direction (direction away from the end wall 23 of the cylinder 20), and the second inclined portion is inclined in the damper braking direction (the end wall 23 of the cylinder 20). ), and the protrusion of the piston is positioned in the direction opposite to that in FIG. 6 with the intermediate portion of the friction member sandwiched become.

(Effect)
Next, the effects of the damper 10 having the structure described above will be described.

In this damper 10, when one member (fixed body, etc.) and the other member (opening/closing body, etc.) are close to each other, as shown in FIG. Adjacent to the end wall 23, the shaft portion 50 is retracted into the cylinder 20 for a predetermined length, and as shown in FIG. It is separated from the first inclined portion 91 of the portion 90 . In this state, the outer peripheral surfaces 96, 96 of the pair of second inclined portions 95, 95 of the friction portion 90 of the friction member 70 are in pressure contact with the inner peripheral surface 21a of the wall portion 21 of the cylinder 20. As shown in FIG.

In this state, when the other member moves away from the other member (when the openable member opens from the fixed member), the head 60 of the piston 40 moves as indicated by the arrow F1 in FIG. , slide away from the end wall 23 of the cylinder 20 (the piston 40 slides in the cylinder 20 in the damper braking direction), and the shaft 50 is pulled out from the opening 25 side of the cylinder 20 (Fig. 9).

Then, while the outer peripheral surfaces 96, 96 of the pair of second inclined portions 95, 95 of the friction member 70 are in sliding contact with the inner peripheral surface 21a of the cylinder 20, the piston 40 slides (see FIG. 9). The outer peripheral edge portion 57a of the pressing protrusion 57 contacts and presses the back surfaces 91a, 91a of the pair of first inclined portions 91, 91, and the pair of second inclined portions 91a, 91a are pushed through the first inclined portions 91,91. 95, 95 are pushed apart (see FIGS. 10(b) and 10(c)).

At this time, when the pressing load of the pressing protrusion 57 is large, as shown in FIG. is pressed against the inner peripheral surface 21a of the . On the other hand, when the pressing load of the pressing protrusion 57 is lower than in the case of FIG. 10(b), as shown in FIG. Only the tip portion is pressed against the inner peripheral surface 21a of the cylinder 20 . As a result, a frictional force is applied between the inner peripheral surface 21a of the cylinder 20 and the second inclined portion 95, and a braking force is applied to the piston 40 by a friction damper.

Further, as described above, when the piston 40 slides in the damper braking direction in the cylinder 20, the seal ring 45 moves toward the flange portion 63 of the head portion 60 (see the phantom line in FIG. 7), and the air flows. Since the path R3 is blocked and the pressure in the air chamber R1 of the cylinder 20 is reduced, the braking force is also applied to the piston 40 by the air damper.

As described above, in this embodiment, two damping forces are applied to the piston 40 by the friction damper and the air damper, so that one member can be slowly moved with respect to the other member (fixed damper). You can slowly open the opening and closing body from the body).

On the other hand, when one member is moved in a direction approaching the other member (when the opening/closing member is closed with respect to the fixed member), the head 60 of the piston 40 moves as indicated by the arrow F2 in FIG. , toward the end wall 23 of the cylinder 20 (the piston 40 slides back within the cylinder 20), and the shank 50 is pushed into the cylinder 20. As shown in FIG.

Then, while the outer peripheral surfaces 96, 96 of the pair of second inclined portions 95, 95 of the friction member 70 are in sliding contact with the inner peripheral surface 21a of the cylinder 20, the piston 40 slides, and the pressing projection 57 of the piston 40 slides. The outer peripheral edge portion 57a is separated from the rear surfaces 91a, 91a of the pair of first inclined portions 91, 91 . Therefore, the pressing protrusion 57 of the piston 40 does not spread the pair of second inclined portions 95 , 95 via the pair of first inclined portions 91 , 91 .

Further, as described above, when the piston 40 slides in the cylinder 20 in the return direction, the seal ring 45 moves toward the base portion 61 of the head portion 60 (see the phantom line in FIG. 7), thereby opening the air flow path. Since R3 is opened, the air in the first chamber R1 passes through the air flow passage R3 and the gap between the outer surface 83 of the intermediate portion 80 of the friction member 70 and the inner peripheral surface 21a of the cylinder 20, and enters the second chamber R2. Since the air is smoothly exhausted to the side, the braking force of the air damper applied to the piston 40 is quickly released, and one member can be quickly moved with respect to the other member (relative to the fixed body). can quickly close the opening and closing body).

In the damper 10, when the pressing load from the pressing protrusion 57 is large, the contact area between the second inclined portion 95 and the inner peripheral surface 21a of the cylinder 20 is increased as shown in FIG. 10(b). is increased to increase the frictional force on the inner peripheral surface 21a of the cylinder 20, and the damper braking force applied to the piston 40 can be increased. At this time, the intermediate portion 80 of the friction member 70 is spaced apart from the inner peripheral surface 21a of the cylinder 20, and the plurality of friction portions 90 are separated from each other in the circumferential direction of the cylinder 20 via the intermediate portion 80. , so that each friction portion 90 can be easily deformed.

On the other hand, when the pressing load from the pressing protrusion 57 is small, as shown in FIG. By reducing the frictional force with respect to the inner peripheral surface 21a of the piston 40, the braking force of the damper applied to the piston 40 can be reduced.

Further, the second inclined portion 95 extends inclined toward the damper braking direction (see FIG. 6), and when the piston 40 slides in the return direction, the pressing protrusion 57 of the piston 40 is separated, so that the same The second inclined portion 95 is restricted from being pushed and spread so as to be in pressure contact with the inner peripheral surface 21a of the cylinder 20, and the intermediate portion 80 of the friction member 70 is separated from the inner peripheral surface 21a of the cylinder 20. Through the intermediate portion 80, a plurality of friction portions 90 are arranged so as to be divided into a plurality of locations in the circumferential direction of the cylinder 20, and each friction portion 90 is easily deformed, so that the piston 40 can be returned smoothly. be able to.

In the damper 10, as described above, the intermediate portion 80 of the friction member 70 is separated from the inner peripheral surface 21a of the cylinder 20, and the plurality of friction portions 90 are separated from each other via the intermediate portion 80. To obtain a damper 10 in which each friction part 90 can be easily deformed by being arranged so as to be divided into a plurality of parts in the circumferential direction of the cylinder 20, so that the braking force of the damper and the load at the time of return can be easily adjusted. be able to.

In this embodiment, as shown in FIG. 8, the cylinder 20 has arcuate inner peripheral surfaces 21a at at least two opposing locations on the inner periphery thereof. The second inclined portion 95 has an arc-shaped outer peripheral surface 96 that fits the arc-shaped inner peripheral surface 21 a of the cylinder 20 .

According to the above aspect, the second inclined portion 95 of the friction portion 70 can be formed with a shape, width, and length suitable for the arc-shaped inner peripheral surface 21a of the cylinder 20, and the rigidity thereof can be increased. Therefore, the frictional force against the inner peripheral surface 21a of the cylinder 20 can be stabilized.

In addition, when the piston 40 slides in the damper braking direction and the pressing protrusion 57 contacts and presses the first inclined portion 91 to push the second inclined portion 95 wide, the second inclined portion 95 is less likely to warp. Frictional force by the second inclined portion 95 can be reliably applied to the inner peripheral surface 21 a of the cylinder 20 .

Furthermore, in this embodiment, as shown in FIGS. 4 and 10, the intermediate portion 80 is thinner than the friction portion 90 and has a flat plate shape.

According to the above aspect, the intermediate portion 80 is thinner than the friction portion 90 and has a flat plate shape. When the pressing protrusion 57 contacts and presses the first inclined portion 91 by sliding in the direction, the second inclined portion 95 can be pushed out more easily.

In this embodiment, as shown in FIGS. 4 and 10, the intermediate portion 80 has a pair of outer side surfaces 83, 83 parallel to each other and spaced apart from the inner peripheral surface 21a of the cylinder 20. have.

According to the above aspect, the intermediate portion 80 has a pair of outer side surfaces 83, 83 parallel to each other and spaced apart from the inner peripheral surface 21a of the cylinder 20, so that the intermediate portion 80 has a high rigidity. It is lower than the friction portion 90, so that the second inclined portion 95 of the friction portion 90 can be further expanded during damper braking, and the gap between the outer surface 83 of the intermediate portion 80 and the inner peripheral surface 21a of the cylinder 20 is increased. That is, by increasing the area of the air circulation passage, the air circulation in the cylinder 20 can be smoothly performed.

Furthermore, in this embodiment, the piston 40 is provided with a seal portion (seal ring 45) that is in close contact with the inner peripheral surface 21a of the cylinder 20 to provide airtightness. A first chamber R1 located on the pushed side of the piston 40 and a second chamber located on the pulled out side of the piston are formed on the boundary of the piston 40 (see FIGS. 6 and 9). An air flow passage is provided to allow the first chamber R1 and the second chamber R2 to communicate with each other, and the sealing portion closes the air flow passage when the piston 40 slides in the damper braking direction and moves in the return direction. It is configured to open the airflow passage when sliding.

According to the above aspect, the braking force due to the frictional force of the second inclined portion 95 of the friction portion 80 of the friction member 70 against the inner peripheral surface 21a of the cylinder 20, and the air flow path and the seal portion that opens and closes the air flow path Since the piston 40 has two damping force imparting structures of a friction damper and an air damper, the damper damping force imparted to the piston 40 can be further increased.

(Another embodiment of the damper)
FIG. 11 shows another embodiment of the damper according to the invention. In addition, the same code|symbol is attached|subjected to the substantially same part as the said embodiment, and the description is abbreviate|omitted.

This damper differs from the above embodiment in the shape of the friction portion 90A of the friction member 70A.

That is, a second inclined portion 95 extending inclines toward the damper braking direction from the middle of the extending direction of the first inclined portion 91 of the friction portion 90A, and a second inclined portion 95 extending in the middle of the extending direction of the first inclined portion 91 of the friction portion 90A. The second inclined portion 95 and the extended portion 97 slide on the inner peripheral surface 21 a of the cylinder 20 . are designed to come into contact with each other. That is, as shown in FIG. 11, when the friction member 70A is viewed from the side, the friction portion 90A includes a second inclined portion 95 and a second inclined portion 95 extending in a bifurcated manner from an intermediate portion of the first inclined portion 91 in the extending direction. It has a substantially Y shape formed by an extension 97 .

In this embodiment, when the pressing load of the pressing protrusion 57 is large, as shown in FIG. Only the outer surface of the connecting portion (boundary portion) of 95 and 97 is left and pressed against the inner peripheral surface 21a of the cylinder 20 . On the other hand, when the pressing load of the pressing protrusion 57 is lower than in the case of FIG. 11A, as shown in FIG. The extension direction tip portion of the surface 98 and the vicinity thereof are pressed against the inner peripheral surface 21a of the cylinder 20 . As a result, a frictional force is applied between the inner peripheral surface 21a of the cylinder 20, the second inclined portion 95 and the extension portion 97, and a braking force is applied to the piston 40 by the friction damper. The pressure contact area of the second inclined portion 95 and the extended portion 97 with respect to the inner peripheral surface 21a of the cylinder 20 shown in FIG. 11(a) is is larger than the pressure contact area of the second inclined portion 95 and the extension portion 97 with respect to the .

In the case of this embodiment, not only the second inclined portion 95 but also the extended portion 97 are in pressure contact with the inner peripheral surface 21a of the cylinder 20, so that the braking force of the friction damper can be further increased. can.

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

10 damper 20 cylinder 23 end wall 25 opening 30 cap 40 piston 45 seal ring (seal portion)
50 shaft portion 57 pressing projection (projection)
60 head 70 friction member 80 intermediate portion 90 friction portion 91 first inclined portion 95 second inclined portion R1 first chamber R2 second chamber

Claims (5)

A damper that is attached between a pair of members that approach and separate from each other and applies a braking force when the pair of members approach or separate,
a cylindrical cylinder whose end forms an opening;
a piston having a shaft extending a predetermined length and slidably inserted into the cylinder;
a friction member attached to the piston;
The friction member is arranged so as to be divided into a plurality of locations in the circumferential direction of the cylinder via an intermediate portion that is attached to the outer periphery of the shaft portion while being spaced from the inner peripheral surface of the cylinder, and the intermediate portion. and a plurality of friction portions that are in sliding contact with the inner peripheral surface of the cylinder,
Each friction portion includes a first inclined portion extending from the intermediate portion in a direction opposite to the damper braking direction of the piston, and a first inclined portion extending in the damper braking direction of the piston from the first inclined portion. and a second inclined portion that extends obliquely and is in sliding contact with the inner peripheral surface of the cylinder,
The piston has a projection that contacts and presses the first inclined portion when sliding in the damper braking direction, and separates from the first inclined portion when sliding in the return direction. ,
The second inclined portion is configured to be pushed and spread through the first inclined portion so as to come into pressure contact with the inner peripheral surface of the cylinder when the first inclined portion is pressed by the protrusion. When the pressing load from the protrusion to the first inclined portion is large, the contact area with the inner peripheral surface of the cylinder increases, and when the pressing load is small, the contact area with the inner peripheral surface of the cylinder increases. A damper characterized by a reduced contact area. The cylinder has arcuate inner peripheral surfaces at at least two opposing locations on its inner periphery,
2. The damper according to claim 1, wherein the second inclined portion of the friction portion has an arcuate outer peripheral surface that fits the arcuate inner peripheral surface of the cylinder. 3. A damper according to claim 1, wherein said intermediate portion is thinner than said friction portion and has a flat plate shape. The damper according to any one of claims 1 to 3, wherein the intermediate portion has a pair of outer side surfaces parallel to each other and spaced apart from the inner peripheral surface of the cylinder. The piston is provided with a seal portion that is in close contact with the inner peripheral surface of the cylinder to provide airtightness,
A first chamber located on the pushing side of the piston and a second chamber located on the pulling side of the piston are formed in the cylinder with the seal portion as a boundary,
Further, the piston is provided with an air flow passage that allows the first chamber and the second chamber to communicate with each other,
The sealing portion is configured to close the air flow passage when the piston slides in the damper braking direction and open the air flow passage when the piston slides in the return direction. A damper according to any one of the preceding claims.

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