JP6479234B2 - Damper - Google Patents

Description

  The present invention relates to an improvement of a damper that generates a braking force by operation of a piston.

   In an air damper device comprising a cylindrical rod body with a rod inner end as a piston portion and a cylindrical cylinder body that can reciprocate the rod body, the rod body penetrates the rod body in the diameter direction. In addition to providing a groove part, a pin body passed through the groove part is provided on the open end side of the cylinder body to prevent the rod body from falling off the cylinder body (Patent Document 1, FIG. 7, (See FIG. 8).

  In this Patent Document 1, the pin body is combined with the cylinder body by pressing both ends of the pin body into through holes provided in the cylinder body, and the pin body has a function more than the function of preventing the rod body from falling off. Not.

JP 2012-237407 A

  The main problem to be solved by the present invention is to make it possible to appropriately reduce the thickness of this type of damper.

In order to achieve the above object, according to the present invention, the damper comprises a piston having a rod and a cylinder for housing the piston, and is a thin type that generates a braking force by the movement or relative movement of the piston. A damper,
The cylinder includes a width side wall portion and a thickness side wall portion, is thin and has a flat cross-sectional shape in a direction perpendicular to the moving direction of the piston , and a pair of the cylinders across the width side wall portion on the open side thereof . The connection part which maintains the distance between width side wall parts constant shall be included.

  According to such a configuration, firstly, the rigidity of the open side of the cylinder can be improved as much as possible, and secondly, the damper always exhibits the expected performance with respect to the distance between the pair of width side walls. Further, it is possible to prevent the cylinder from being deformed by an environmental change such as an external force or a temperature change.

  One of the preferred embodiments of the present invention is that the rod is provided with a long hole along the moving direction through which the connecting portion passes. Such a long hole can prevent the piston from coming out of the cylinder, and can smoothly move the piston side.

  In this case, it is one of preferred embodiments of the present invention that one end of the elongated hole is further constituted by the piston. In this case, the moving distance of the piston in the cylinder can be maximized.

  Moreover, it is preferable that this connection part shall connect the position of one width direction middle of the said width side wall part, and the position of the other width direction middle of the said width side wall part. This is one of the embodiments.

  The connecting portion may be configured by a pin body that is passed through a through hole provided in the width side wall portion and has a crimped portion formed at an end portion.

  The connecting portion is formed of a part of the width side wall portion divided by a split groove provided on one side of the width side wall portion, and is formed on a thin base portion that can be bent and the other side of the width side wall portion. It may be configured by a movable piece having a free end that can be engaged with the engaged portion.

  In addition, the cylinder is configured by combining a first part including one of the width side walls and a second part including the other of the width side walls, and the first part and the second part. In some cases, a protruding portion that is abutted by the combination and serves as the connecting portion is formed.

  According to the present invention, the connecting portion can maintain the rigidity on the open side of the cylinder and the distance between the pair of width side wall portions constant, and further, the cylinder can be deformed by an environmental change such as an external force or a temperature change. Therefore, the damper can be appropriately thinned.

FIG. 1 is a perspective view of a damper (first example) according to an embodiment of the present invention. FIG. 2 is an exploded perspective view of the first example. FIG. 3 is a perspective view of a piston and a rod constituting the first example. FIG. 4 is a cross-sectional configuration diagram of the first example. FIG. 5 is an enlarged cross-sectional configuration diagram of the main part of the first example, showing a state when the piston moves forward. FIG. 6 is an enlarged cross-sectional configuration diagram of the main part of the first example, showing a state when the piston moves forward. FIG. 7 is an enlarged cross-sectional configuration diagram of the main part of the first example, showing a state when the piston moves backward. FIG. 8 is a perspective configuration diagram of a cylinder constituting the damper (second example) according to the embodiment of the present invention. FIG. 9 is a cross-sectional view of a main part of a cylinder constituting the second example. FIG. 10 is a cross-sectional view of the main part of the second example. FIG. 11 is an end surface configuration diagram of a cylinder constituting the damper (third example) according to the embodiment of the present invention, and shows a state before the first portion and the second portion constituting the cylinder are combined. . FIG. 12 is an end face configuration diagram of the third example. FIG. 13 is a perspective configuration diagram of a main part of a cylinder constituting the damper (fourth example / reference example ) according to the embodiment of the present invention.

  Hereinafter, typical embodiments of the present invention will be described with reference to FIGS. The damper according to this embodiment generates a braking force in the movement or relative movement of the piston P constituting the damper, and typically includes a movable part to be braked (not shown). ), The movement of the braking object by applying the braking force to the movement of the braking object is slow, high-class, moderate, or It is used in order not to make it outrageous.

  Such a damper comprises a piston P provided with a rod 1 and a cylinder S in which the piston P is accommodated. Typically, such a damper links either one of the rod 1 and the cylinder S directly or indirectly to the braking object side, and directly or indirectly connects the other of these to the side that supports the braking object movably. By linking, it is combined with an article having such a braking object.

  The cylinder S has a cylindrical shape with one end open and the other end closed. Although illustration is omitted, the cylinder S may have a configuration in which one end of a cylindrical body whose both ends are open is closed by another component. The cylinder S has a flat cylindrical shape with a significantly reduced thickness. More specifically, the cylinder S has a width side wall portion 7 and a thickness side wall portion 8 and has a cross-sectional shape in a direction orthogonal to the moving direction x of the piston P, that is, a cross-sectional shape orthogonal to the cylinder axis. The substantially square shape is flat.

  The thickness side wall portion 8 has a curved shape with the outer side of the cylinder S being the curved outer side.

  A bracket portion 10 for the linkage is formed outside the closed end 9 of the cylinder S.

  Moreover, this cylinder S has the connection part 12 ranging between the said width side wall parts 7 in the open | release side. As a result, the cylinder S has a flat cylindrical shape, but firstly the rigidity on the open side can be improved as much as possible. Second, the distance between the pair of the side wall portions 7 can be determined by the damper. It can be kept constant so that the performance of the period is always exhibited.

  In the first example shown in FIGS. 1 to 7, the second example shown in FIGS. 8 to 10, and the third example shown in FIGS. 11 and 12, the connecting portion 12 is one of the width side wall portions 7. The middle position in the width direction and the other middle position in the width direction of the width side wall portion 7 are connected to each other. In particular, in the first example, the second example, and the fourth example, the connecting portion 12 also has a function of preventing deformation in a direction in which the distance between the pair of the side wall portions 7 and 7 of the cylinder S is increased. Yes.

  In the first example, the connecting portion 12 is constituted by a pin body 120 that is passed through a through hole 7a provided in the width side wall portion 7 and has a crimped portion 120c formed at an end portion. In the first example, the pin body 120 includes a disk-shaped head portion 120a and a columnar shaft portion 120b. Each of the pair of width side wall portions 7 and 7 is formed with a through hole 7a having a size that allows the shaft portion 120b to pass therethrough but does not allow the head portion 120a to pass therethrough. In this first example, the rod 1 is formed with a long hole 1b along the moving direction x of the piston P through which the leg portion of the connecting portion 12 thus configured passes. In this first example, a portion of the piston P and the rod 1 positioned at least on the piston P side is accommodated in the cylinder S, and the through holes 7a and the elongated holes 1b of the pair of the side wall portions 7 and 7 are placed. The end portion of the shaft portion 120b protruding from the other through hole of the wide side wall portion 7 is crimped from the state where the shaft portion 120b is inserted through the shaft portion 120b, thereby forming a crimped portion 120c having a diameter larger than that of the through hole 7a. Thus, the connecting portion 12 is formed in the cylinder S.

  In the second example, the connecting portion 12 is formed of a part of the width side wall portion 7 divided by a split groove 7b provided on one side of the width side wall portion 7, and bendable thin base 121a; The movable piece 121 includes a free end 121b that can be engaged with an engaged portion 7e formed on the other side of the width side wall portion 7. The movable piece 121 includes a pair of elongated first through holes 7c, 7c along the cylinder axis of the cylinder S, and holes positioned on the closed end 9 side of the pair of first through holes 7c, 7c. It is comprised by one part of the said width side wall part 7 divided by the 2nd through-hole 7d ranging between ends. A groove is formed in the outer surface of the width side wall portion 7 between the pair of first through holes 7c, 7c between the hole ends positioned on the open end 11 side of the cylinder S. The open end 11 side of the cylinder S is a thin base 121a. The engaged portion 7e is configured by a through hole that can receive the free end 121b of the movable piece 121 provided on the other side of the width side wall portion 7 at a position directly below the thin base 121a of the movable piece 121. Even in this second example, the rod 1 is formed with a long hole 1b along the moving direction x of the piston P through which the movable piece 121 of the connecting portion 12 thus configured passes. In this second example, the movable piece 121 is moved into the cylinder S while the thin base 121a is elastically deformed from the state where the piston P and the position located at least on the piston P side of the rod 1 are accommodated in the cylinder S. When the inner end of the movable piece 121 is pushed inward, the free end 121b of the movable piece 121 enters the engaged portion 7e while slightly elastically deforming the terminal 121c, and then the step of the entrance side of the engaged portion 7e is restored by elastic recovery. By engaging with the portion 7f, the connecting portion 12 is formed in the cylinder S.

  In the third example, the cylinder S is configured by combining a first portion S ′ including one of the width side wall portions 7 and a second portion S ″ including the other of the width side wall portions 7. In this third example, the cylinder S is divided into the first portion S ′ and the second portion S ″ at a position in the middle of the thickness side wall portion 8 in the thickness direction. The first part S and the second part S ″ are connected via a thin part Sa formed on one side of the thick side wall part 8, and the wide side wall of the first part S ′ while elastically deforming the thin part Sa. When the portion 7 and the width side wall portion 7 of the second portion S ″ are combined so as to be parallel to each other, they are abutted on the side opposite to the thin-walled portion Sa and the other side of the thickness side wall portion 8 is formed. ing. In this abutted portion Sb, the first part and the second part S ″ are welded in an airtight state. In this third example, the first part S ′ and the second part S ″ are joined together. Each of the protrusions 122 which are abutted by the combination and become the connecting portion 12 is formed. The projecting portions 12 of the first portion S ′ and the second portion S ″ each have a step shape having an upper step 122a and a lower step 122b at the leading ends thereof and a step 122c therebetween, and the first portion S ′ is obtained by the above-mentioned joining. The upper stage 122a is in contact with the lower stage 122b of the second part S ", and the lower stage 122b of the first part S 'is in contact with the upper stage 122a of the second part S", so that the columnar connecting portion 12 is formed. Even in the third example, the rod 1 is formed with a long hole 1b along the moving direction x of the piston P that allows the connecting portion 12 thus configured to pass (FIG. 12). In the third example, the piston S and the rod 1 are placed in the cylinder S at least on the piston P side, and the binding is performed so that the protrusion passes through the long hole 1b. To do More, so as to form a connecting portion 12 to the cylinder S.

  In these first to third examples, the connecting portion 12 can maintain the combined state of the cylinder S and the piston P side and guide the movement on the piston P side.

  On the other hand, in the fourth example shown in FIG. 13, the connecting portion 12 is provided at two locations, and the rod 1 is sandwiched between the two connecting portions 12 and 12. In the fourth example, the connecting portions 12 are provided on both sides of the cylinder S in the middle in the width direction. The distance between the two connecting portions 12 is substantially the same as the width dimension of the rod 1 and is smaller than the dimension of the piston P, which will be described later, in the direction perpendicular to the moving direction x. In the illustrated example, the connecting portion 12 of the fourth example is configured by a pin body 120 similar to the connecting portion 12 of the first example. In the fourth example, the two connecting portions 12 and 12 can first improve the rigidity on the open side of the cylinder S, and secondly, the pair of width side walls 7 and 7. The distance between them can be maintained more firmly and constant so that the damper always exhibits the desired performance, and third, the combined state of the cylinder S and the piston P side can be maintained by the connecting portion 12, and the piston The movement on the P side can be guided. In the fourth example, the rod 1 does not require the long hole 1b in the first to third examples. In addition, although illustration is abbreviate | omitted, the said connection part 12 is provided only in the one side which pinched | interposed the position of the center of the width direction of the cylinder S, and the combined state of piston P is maintained by the connection part 12 of one place. You can also.

  In addition, since the structure of the rod 1 and piston P of said 2nd example-4th example is the same as that of a 1st example, or substantially the same, it is based on FIGS. 1-7 which show a 1st example below. I will explain.

  The rod 1 has a long rod shape in the moving direction of the piston P. A bracket portion 1a for the linkage is formed at the outer end of the rod 1 located outside the cylinder S.

  The rod 1 includes a long hole 1b along the moving direction that allows the connecting portion 12 to pass therethrough. In this embodiment, one end of the elongated hole 1b is constituted by the piston P. Specifically, in this embodiment, one of the closed hole ends of the long hole 1b that is always positioned in the cylinder S that is one end of the long hole 1b is a part of the piston P. It is located in the second flange 5 to be described later. Accordingly, in this embodiment, the long hole 1b prevents the piston P from coming out of the cylinder S, and the movement of the piston P in the cylinder S is made smooth while the piston P side moves smoothly. It is designed to maximize the distance.

  The piston P includes a seal member 2 for the inner wall of the cylinder S, and a slider 3 that is slidable with respect to the piston P and that contacts the inner wall of the cylinder S with a predetermined frictional force.

  In the illustrated example, the piston P includes a first flange 4 that faces the closed end 9 of the cylinder S, and a second flange 5 that holds the seal member 2 and the slider 3 between the first flange 4. ing. The second flange 5 is located behind the first flange 4, that is, on the open end 11 side of the cylinder S. The first flange 4 and the second flange 5 both have a cross-sectional outline shape in a direction orthogonal to the moving direction x of the piston P, that is, the direction along the cylinder axis of the cylinder S, and the cross-section of the cylinder S in the same direction. The shape is complementary to the contour shape, whereby the piston P is guided by the inner wall of the cylinder S so as to reciprocate in the direction along the cylinder axis of the cylinder S.

  More specifically, the second flange 5 is formed at the inner end of the rod 1. The first flange 4 is formed on the head part 6 which is separate from the rod 1. The head part 6 has a plate-like body portion 6 a whose plate surface faces the width side wall portion 7 of the cylinder S. The first flange 4 with the flange end positioned on the outer side of the outer surface of the barrel portion 6a at each position around the barrel portion 6a is integrally formed on the side of the barrel portion 6a facing the closed end 9 of the cylinder S. Is formed. Further, an end portion of the trunk portion 6a facing the open end 11 of the cylinder S, which is located on the cylinder axis of the cylinder S, includes a head portion 6c and a neck portion 6d. A male joint portion 6b integrated with the trunk portion 6a via the portion 6d is formed. At a position on the cylinder axis of the cylinder S in the second flange 5, a first recess 5b for receiving and holding the head 6c of the male joint portion 6b and a neck portion 6c of the male joint portion 6b are provided. A female joint portion 5a is formed which comprises a second recess 5c which is received and held and opened outward at the end of the second flange 5 facing the closed end 9 of the cylinder S. In this embodiment, the seal member 2 and the slider 3 each having a flat ring shape are combined with the head part 6 so as to surround the body portion 6a of the head part 6, and then the male part of the head part 6 is used. By fitting the joint portion 6 b into the female joint portion 5 a of the second flange 5, a piston P configured to hold the seal member 2 and the slider 3 between the first flange 4 and the second flange 5 is formed. It has become.

  The seal member 2 is typically made of rubber or plastic having rubber-like elasticity, and has a flat ring shape. By inserting the body portion 6a of the head part 6 into the seal member 2 from the male joint portion 6b side, the head part 6 and the seal member 2 are combined. In the illustrated example, the seal member 2 has a front end surface 2 a for the first flange 4, an inner surface portion 2 b for the outer surface of the head part 6, and an outer surface portion 2 c for the inner wall of the cylinder S. On the side of the seal member 2 facing the open end 11 of the cylinder S, a circumferential groove 2d is formed between the inner surface portion 2b and the outer surface portion 2c. The outer surface side across the circumferential groove 2d extends toward the open end 11 side of the cylinder S over the entire circumferential direction of the seal member 2, whereby the seal member 2 includes a skirt-like portion 2e. In the moving direction x of the piston P, the outer surface portion 2c of the seal member 2 is larger than the inner surface portion 2b. The outer surface portion 2c of the seal member 2 is inclined so as to gradually increase the thickness of the seal member 2 from the front end surface 2a toward the terminal 2f of the skirt-shaped portion 2e. Further, a circumferential protrusion 2g is formed on the front end surface 2a of the seal member 2.

  The slider 3 is typically made of plastic and has a flat ring shape. From the state in which the head part 6 and the seal member 2 are combined as described above, the body part 6a of the head part 6 is inserted into the inside of the slider 3 from the male joint part 6b side. 3 is combined. In the illustrated example, the slider 3 has a short cylindrical shape in which the cross-sectional outline shape orthogonal to the moving direction x of the piston P is complementary to the cross-sectional outline shape of the body portion 6a of the head part 6 in the same direction. Base 3a and a lip 3d formed integrally with the outside of the base 3a. In the illustrated example, the lip 3d is a circular fin-like body formed so as to surround the base 3a. The lip 3d is a base portion integrated with the outer surface portion of the base 3a between the front end 3b located on the seal member 2 side of the base 3a and the rear end 3c located on the open end 11 side of the cylinder S. 3e and an extending portion 3f extending from the base portion 3e toward the open end 11 of the cylinder S. A shoulder 3h is formed between the base 3e and the extension 3f. The extension 3f has an inclination that gradually increases the distance from the base 3a as it goes from the shoulder 3h toward the terminal 3g.

  Between the first flange 4 and the second flange 5, the seal member 2 and the slider 3 are both held in a state where slight movement along the moving direction x of the piston P is allowed. The outer surface portion 2c of the seal member 2 is in contact with the inner wall of the cylinder S over the entire circumference, and the extending portion 3f of the slider 3 is also in contact with the inner wall of the cylinder S on the terminal 3g side over the entire circumference. Yes. Further, the portion between the front end 3b of the base 3a of the slider 3 and the base 3e of the lip 3d is located inside the skirt-like portion 2e of the seal member 2, and the shoulder 3h of the lip 3d of the slider 3 is It faces the terminal 2f of the skirt-like portion 2e of the seal member 2 (FIGS. 4 to 6).

  In this embodiment, when the braking force is generated, the slider 3 comes into pressure contact with the seal member 2, and the portion of the seal member 2 that contacts the inner wall of the cylinder S is outside the cylinder S. It is designed to deform toward.

  In the illustrated example, when the piston P moves forward in a direction away from the closed end 9 of the cylinder S, the chamber C formed between the piston P and the closed end 9 becomes a negative pressure, thereby a part of the braking force. Resistance due to pressure change is generated (FIGS. 4 and 5). At this time, the slider 3 deforms the sealing member 2 as described above to increase the frictional force between the sealing member 2 and the cylinder S, thereby generating a frictional resistance that becomes a part of the braking force. (FIGS. 4 and 5).

  In the illustrated example, when the piston P is moved forward, the slider 3 becomes difficult to move in the forward movement direction due to the shape of the lip 3d, so that the shoulder 3h of the slider 3 is the skirt-shaped portion 2e of the seal member 2. The circumferential protrusion 2g formed on the front end surface 2a of the seal member 2 is brought into close contact with the first flange 4 so that the space between the front end surface 2a and the first flange 4 is sealed. The shape portion 2e is deformed outward to seal between the outer surface portion 2c of the seal member 2 and the inner wall of the cylinder S (FIGS. 4 and 5). Thus, in the example shown in the figure, when the piston P is moved forward, the ventilation to the chamber C is performed at the first flange 4 at a position located on the cylinder axis of the cylinder S in the head part 6 constituting the piston P. Is limited to an air passage formed by a groove 6e (see FIGS. 2 and 5) formed from the edge of the cylinder 6a toward the open end 11 of the cylinder S in the body 6a. Resistance is generated. The frictional resistance is generated by the outward deformation of the skirt-like portion 2e of the seal member 2. That is, the slider 3 includes a pressure contact portion that is pressed against the seal member 2 from the rod 1 side. In the illustrated example, the shoulder portion 3h functions as this pressure contact portion.

  In this embodiment, the deformation amount of the seal member 2 increases according to the operating speed of the piston P. Therefore, the damper according to this embodiment is a speed response type or load response type damper that changes the braking force in accordance with the moving speed of the braking target to be braked.

  In the damper according to this embodiment, since the braking force is covered by the resistance due to the pressure change and the frictional resistance, the movement of the braking target can be properly controlled in the entire process. That is, according to the damper according to this embodiment, there is a situation in which the braking target stops in the course of movement, or even starts to return to the position before movement from the middle of movement. It can be prevented as much as possible. In addition, the damper according to this embodiment has a feature that it is easy to generate a desired braking force even if the cross-sectional area of the cylinder S is reduced, and it is easy to reduce the size and thickness.

  On the other hand, in the illustrated example, when the piston P moves backward toward the closed end 9 of the cylinder S, the chamber C is unlikely to be positive pressure, and at this time, the frictional resistance is also reduced. (FIG. 7). In the illustrated example, when the piston P is double-acted, the seal member 2 and the slider 3 move to the second flange 5 side, and a gap y is formed between the first flange 4 and the front end surface 2a of the seal member 2. At the same time, the shape of the lip 3d makes it easier for the slider 3 to move in the backward movement direction of the piston P, so that the slider 3 is not pressed against the seal member 2 and between the seal member 2 and the inner wall of the cylinder S. The frictional resistance is not increased. The chamber C is also communicated through a gap y between the first flange 4 and the front end surface 2a of the seal member 2 in addition to the air passage formed by the groove 6e. Further, in the illustrated example, a groove 2h is formed on the outer surface of the seal member 2 along the moving direction x of the piston P. The groove 2h opens the groove end on the chamber C side, and the open end 11 of the cylinder S is opened. Although the groove end on the side is closed, when the piston P returns, a part of the seal member 2 is deformed inward at the position where the groove 2h is formed due to an increase in pressure on the chamber C side. Exhaust gas comes from C. Accordingly, in the illustrated example, when the piston P moves backward, the damper does not generate a special braking force.

  As a matter of course, the present invention is not limited to the embodiment described above, but includes all embodiments that can achieve the object of the present invention.

P Piston P
H Housing 1 Rod 1
7 Wide side wall portion 8 Thickness side wall portion x Movement direction 12 Connection portion

Claims (6)

A thin damper comprising a piston having a rod and a cylinder for housing the piston, and generating a braking force by the movement or relative movement of the piston,
The cylinder includes a width side wall portion and a thickness side wall portion, is thin and has a flat cross-sectional shape in a direction perpendicular to the moving direction of the piston, and a pair of the cylinders across the width side wall portion on the open side thereof. It has a connecting part that keeps the distance between the wide side wall parts constant,
The rod is a damper comprising an elongated hole along the moving direction through which the connecting portion passes . The damper according to claim 1 , wherein one end of the elongated hole is configured by the piston .   The damper according to claim 1 or 2, wherein the connecting portion connects a position in the middle of one width direction of the width side wall portion and a position in the middle of the other width direction of the width side wall portion. .   The said connection part is comprised by the pin body by which it passed through the through-hole provided in the said width | variety side wall part, and the crimp part was formed in the edge part of any one of Claims 1-3. Damper.   The connecting portion is formed of a part of the width side wall portion divided by a split groove provided on one side of the width side wall portion, and has a bendable thin base portion and an engaged portion formed on the other side of the width side wall portion. The damper of any one of Claims 1-3 comprised by the movable piece provided with the free end which can be engaged with a joint part. The cylinder is configured by combining a first portion including one of the width side wall portions and a second portion including the other of the width side wall portions,
The damper according to any one of claims 1 to 3, wherein the first portion and the second portion are each abutted by the combination to form a protruding portion serving as the connecting portion.

Images