WO2014013651A1

WO2014013651A1 - Damper

Info

Publication number: WO2014013651A1
Application number: PCT/JP2013/002863
Authority: WO
Inventors: ヨンユンチェ; ジュンヒョンチョ; 敦大城
Original assignee: 株式会社パイオラックス
Priority date: 2012-07-16
Filing date: 2013-04-26
Publication date: 2014-01-23
Also published as: KR20140010678A

Abstract

A clip (20) is provided with: a first plate section (22) which has a free end at one end thereof and which is inserted in a mounting hole; a second plate section (24) which has a free end at one end thereof and which is inserted in a mounting hole; and a flange section (26) which connects the other end of the first plate section (22) and the other end of the second plate section (24) in such a manner that the first plate section (22) and the second plate section (24) face each other, the flange section (26) having an insertion hole for allowing a pin member (60) to be inserted therein, the flange section (26) being adapted to be in contact with the front surface side of a mounting member. The first plate section (22) and the second plate section (24) each have: a wide section which is formed on the other end side; and a narrow section which is formed at a position closer to the one end side than the wide section so as to be narrower than the wide section in the width direction. The opposing pair of the narrow sections each have a near section which is bent on the one end side in such a manner that each of the near sections approaches each other. The pin member (60) separates the near sections from each other and spreads the first plate section (22) and the second plate section (24) away from each other, thereby engaging the first plate section (22) and the second plate section (24) with the edge on the rear side of the mounting hole.

Description

Damper

The present invention relates to a damper that generates a damping force in accordance with the movement of a piston.

Damper is provided on the lid member of the vehicle glove box. By this damper, when the lid member is opened, the lid member is gently opened, and when the lid member is closed, it is easily closed without much resistance.

For example, Patent Document 1 discloses an air damper including a cylinder, a piston that is reciprocally inserted into the cylinder, and an orifice that is formed through the piston in the axial direction. This air damper is a ventilation path other than the orifice formed on the surface of the piston, and has a ventilation groove having one end connected to the orifice and the other end opened outside the closed region by a valve. The ventilation groove vents the orifice when the orifice is closed by the valve, and prevents the damping force from being excessively increased due to the orifice being completely closed.

Japanese Utility Model Publication No. 2-58137

In the technique described in Patent Document 1, the load responsiveness of the air damper is improved by forming a ventilation groove. However, the change in load responsiveness is small only by forming the ventilation groove, and the load responsiveness is further improved. A damper is desired.

The present invention has been made in view of such problems, and an object thereof is to provide a damper having improved load response.

In order to solve the above-described problems, a damper according to an aspect of the present invention includes a cylinder, a reciprocating insertion into the cylinder, the cylinder being divided into a first chamber and a second chamber, and the first chamber and the second chamber being separated from each other. A piston having a communication hole communicating therewith, and a valve attached to the communication hole. The valve has a cover portion that covers the communication hole from the second chamber side. The piston has a groove formed from an inner region covered by the cover part to an outer region outside the cover part. When the pressure in the first chamber decreases due to the movement of the piston, the cover part is bent into the groove part to narrow the opening of the flow path in the groove part, and the groove part is inclined so that the depth becomes shallower from the outer region toward the inner region. Formed.

According to this aspect, the opening area of the flow path can be changed by the cover part entering the groove part due to the negative pressure in the first chamber. In addition, since the groove portion is formed to be inclined so that the depth becomes shallower from the outer region toward the inner region, the flow passage on the outer diameter side is reduced even if the amount of the cover portion inner diameter side that is difficult to bend is sucked into the groove portion. The opening area can be reduced similarly to the opening area. As a result, as the negative pressure in the first chamber increases, the inner diameter side of the cover portion gradually enters the groove portion, and the narrowing of the opening area of the flow path continues from the outer diameter to the inner diameter side, thereby gradually reducing the resistance of the flow path. And the load responsiveness can be improved.

According to the present invention, the load responsiveness of the damper can be improved.

It is a perspective view of the damper concerning an embodiment. It is a figure for demonstrating a piston rod. It is a figure for demonstrating a valve | bulb. It is a figure for demonstrating the positional relationship of a piston and a valve | bulb. It is a figure for demonstrating the effect | action to the groove part of a valve | bulb when the negative pressure of a 1st chamber is relatively weak. It is a figure for demonstrating the effect | action to the groove part of a valve | bulb when the negative pressure of a 1st chamber is relatively strong. It is a figure which shows the damping-force characteristic of each damper which has a shape of a different groove part. FIG. 8A shows the communication hole and the attachment hole of the first modification, and FIG. 8B shows the communication hole and the attachment hole of the second modification.

FIG. 1 is a perspective view of a damper 10 according to the embodiment. The damper 10 is attached to a glove box of a vehicle, for example, and applies a damping force to open / close the opening / closing member (lid member) of the glove box. The damper 10 includes a cylinder 20, a piston rod 30, a valve 50 and a seal ring 60.

The cylinder 20 is formed in a bottomed cylindrical shape. A piston rod 30 is inserted into the cylinder 20. The piston rod 30 includes a piston 32 that partitions the inside of the cylinder 20 and a rod 34. A first chamber 22 and a second chamber 24 are formed in the cylinder 20 by the piston 32. A seal ring 60 is provided on the outer periphery of the piston 32 to improve the degree of sealing of the first chamber 22. The second chamber 24 may be open to the outside air.

The rod 34 has one end fixed to the piston 32 and the other end connected directly or indirectly to the opening / closing member. The piston 32 is inserted into the cylinder 20 and reciprocates according to the operation of the opening / closing member. The valve 50 is attached to the piston 32 and covers a communication hole (not shown) formed in the piston 32 from the second chamber 24 side. The valve 50 operates to open the communication hole when gas exits from the first chamber 22 to the second chamber 24 and closes the communication hole when gas enters the first chamber 22 from the second chamber 24. That is, when the piston 32 is pushed and the pressure in the first chamber 22 increases, the damper 10 releases the gas in the first chamber 22 from the communication hole to suppress the damping force, and the piston 32 is pulled and the first chamber 22 When the pressure decreases, the communication hole is closed and the damping force is increased. In the glove box, when the lid member is opened, the piston 32 is pulled and slowly opened, and when the lid member is closed, the piston 32 is pushed and easily closed.

FIG. 2 is a view for explaining the piston rod 30. 2 (a) is a perspective view of the piston rod 30, FIG. 2 (b) is a front view of the piston rod 30, and FIG. 2 (c) is a view of the piston rod 30 shown in FIG. 2 (b). It is sectional drawing of line segment AA. Here, the same or equivalent components and members shown in the drawings are denoted by the same reference numerals, and repeated description thereof is omitted as appropriate.

The piston 32 is formed in a cup shape, and has a disk part 44 and a cylindrical part 46 provided on the outer periphery of the disk part 44. A rod 34 is provided on the surface of the disk portion 44. The front surface of the disk portion 44 is exposed to the outside, and the back surface forms the first chamber 22. A ring holding groove 42 for holding the seal ring 60 is formed on the outer periphery of the cylindrical portion 46.

The disk portion 44 has a communication hole 36 that allows the first chamber 22 and the second chamber 24 to communicate with each other, a mounting hole 38 to which the valve 50 is attached, and a groove portion 40. The groove portion 40 is formed on the surface of the disk portion 44. The surface of the disk part 44 is a surface on the second chamber 24 side. As shown in FIG. 2B, the groove 40 extends radially outward from the periphery of the communication hole 36 and the attachment hole 38.

The communication hole 36 and the mounting hole 38 pass through the disk portion 44 and communicate with the first chamber 22 and the second chamber 24. The communication hole 36 is formed around the attachment hole 38. The groove 40 is separated from the communication hole 36 and the mounting hole 38.

FIG. 3 is a diagram for explaining the valve 50. FIG. 3A is a side view of the valve 50, and FIG. 3B is a cross-sectional view of the valve 50 attached to the piston 32. The valve 50 includes a cover part 52, a shaft part 54, an enlarged diameter part 56, and a step part 58. The valve 50 is formed in an umbrella shape.

The cover part 52 has flexibility and is formed in a circular shape that hangs radially outward from the shaft part 54. A shaft portion 54 is formed at the center of the back surface of the cover portion 52. A diameter-expanded portion 56 that expands in the middle of the shaft portion 54 is formed. The cover part 52 covers the communication hole 36 from the second chamber 24 side.

As shown in FIG. 3 (b), the shaft portion 54 extends from the cover portion 52 toward the first chamber 22. The shaft portion 54 is inserted into the mounting hole 38 and is prevented from coming off by the enlarged diameter portion 56. The step portion 58 formed at the base of the shaft portion 54 restricts the shaft portion 54 from moving too much in the axial direction when the cover portion 52 is sucked by negative pressure.

The outer periphery of the cover part 52 contacts the surface of the piston 32. The inner side of the outer periphery of the cover part 52 is referred to as an inner area on the surface of the piston 32, and the outer side of the outer periphery of the cover part 52 is referred to as an outer area.
The communication hole 36 is located in the inner region. The cover portion 52 is recessed when receiving a negative pressure from the communication hole 36 and floats when receiving a positive pressure to allow air to escape.

FIG. 4 is a diagram for explaining the positional relationship between the piston 32 and the valve 50. 4A is a perspective view of the piston 32 showing the vicinity of the attachment position of the valve 50, and FIG. 4B is a perspective view showing the valve 50 attached to the piston 32. As shown in FIG.

The communication hole 36 is formed in a circular arc shape in the radial direction around the mounting hole 38 while avoiding the groove portion 40. The communication hole 36 is formed so as to surround the attachment hole 38 around the attachment hole 38. Accordingly, the communication hole 36 can be formed largely around the attachment hole 38 within the range of the inner region covered with the cover part 52, and the negative pressure can be easily transmitted to the cover part 52. Further, the size of the communication hole 36 can be secured so that no abnormal noise is generated from the communication hole 36 when air passes. Since the communication hole 36 avoids the groove portion 40, the communication hole 36 and the groove portion 40 are separated from each other.

The communication holes 36 are formed in a pair of arcs surrounding the mounting hole 38 and are divided on the extension of the groove 40. By providing a pair of communication holes 36, the edge of the cylindrical mounting hole 38 can be supported at two locations, and the rigidity of the mounting hole 38 can be improved.

As shown in FIG. 4B, when the valve 50 is attached to the attachment hole 38, the communication holes 36 are all covered with the cover portion 52. That is, the outer diameter of the cover portion 52 is formed to be larger than the outer diameter of the pair of communication holes 36. The groove portion 40 is formed from the inner region covered by the cover portion 52 to the outer region outside the cover portion 52. Thereby, an internal region and an external region are communicated to form a gas flow path.

FIG. 4B shows a state where the cover portion 52 is bent so as to be recessed due to the negative pressure in the first chamber 22. The cover part 52 enters the groove part 40, and the opening of the flow path of the groove part 40 is narrowed. Although the cover part 52 enters the groove part 40, the cover part 52 is not in contact with the corner part 40a of the groove part 40, and a part of the opening of the flow path of the groove part 40 is opened. That is, even when the cover 52 enters the groove 40, a gap remains, and the fluid in the second chamber 24 can pass through the gap into the first chamber 22. Thus, a gas flow path can be secured.

The damper 10 generates a large damping force because the cover portion 52 enters the groove portion 40 and the opening of the flow path is narrowed as the negative pressure in the first chamber 22 increases as the piston 32 moves. By forming the groove portion 40 in this manner, the opening area of the flow path of the groove portion 40 can be adjusted as compared with the case where there is no groove portion 40 and the surface of the piston 32 is flat.

FIG. 5 is a diagram for explaining the action on the groove 40 of the valve 50 when the negative pressure in the first chamber 22 is relatively weak. FIG. 5A is a partial cross-sectional view of the piston 32 and the valve 50, and FIG. 5B is a cross-sectional view of the piston 32 and the valve 50 shown in FIG. FIG. 5C is a cross-sectional view taken along line CC of the piston 32 and the valve 50 shown in FIG.

As shown in FIGS. 5B and 5C, the cross section of the groove 40 is formed in a rectangular shape. As shown in FIG. 5B, when the cover 52 is recessed due to the negative pressure in the first chamber 22 and is bent into the groove 40, the cover 52 leaves a gap at both corners 40 a at the bottom of the groove 40. It abuts on a part of the bottom of the rectangular cross section of the groove 40. Thus, by providing the some corner | angular part 40a, the opening of a flow path is securable.

As shown in FIG. 5A, since the negative pressure in the first chamber is weak, the cover portion 52 enters the groove portion 40 only at the outermost diameter end portion. While the outer diameter side of the cover portion 52 shown in FIG. 5B contacts the bottom of the groove portion 40, the inner diameter side of the cover portion 52 shown in FIG. 5C does not contact the groove portion 40. This is because the outer diameter side of the valve 50 is easily bent and the inner diameter side is not easily bent.

The groove portion 40 on the inner diameter side shown in FIG. 5 (c) is shallower and the groove width is narrower than the groove portion 40 on the outer diameter side shown in FIG. 5 (b). Specifically, the bottom part 40b of the groove part 40 is a smooth inclined surface, and is inclined so that the depth of the groove part 40 becomes shallow inward in the radial direction. In relation to the cover portion 52, the depth of the groove portion 40 decreases from the outer region toward the inner region. Thereby, the inner diameter side of the cover part 52 which is not easily bent easily comes into contact with the groove part 40.

FIG. 6 is a diagram for explaining the action on the groove 40 of the valve 50 when the negative pressure in the first chamber 22 is relatively strong. 6 (a) is a partial cross-sectional view of the piston 32 and the valve 50, and FIG. 6 (b) is a cross-sectional view of the line segment DD of the piston 32 and the valve 50 shown in FIG. 6 (a). FIG. 6C is a sectional view taken along line EE of the piston 32 and the valve 50 shown in FIG.

The negative pressure in the first chamber 22 shown in FIG. 6 (a) is stronger than that shown in FIG. 5 (a), and the cover 52 is greatly bent. Therefore, the cover part 52 contacts the groove part 40 over a predetermined interval from the outermost diameter to the inner diameter side. This is because the inner diameter side of the cover portion 52 is likely to come into contact with the groove portion 40 because the depth of the groove portion 40 becomes shallower inward in the radial direction.

As shown in FIG. 6B and FIG. 6C, the outermost diameter end portion and the inner diameter side of the cover portion 52 abut against the bottom portion 40b of the groove portion 40. Here, if the space | interval which the cover part 52 contact | abuts with the bottom part 40b of the groove part 40 becomes long, the space | interval of the narrowed flow path will become long, movement resistance will become large, and gas will become difficult to pass. Therefore, as the negative pressure in the first chamber 22 becomes stronger, it becomes difficult for gas to pass through and the damping force in the damper 10 can be increased.

The groove portion 40 is formed so that the groove width becomes narrower from the outer region on the surface of the piston 32 toward the inner region, that is, radially inward. In the place where the groove part 40 became shallow, it can suppress that the cover part 52 sticks to the whole bottom part 40b, and can ensure the opening of a flow path. In addition, by securing the opening of the flow path, it is possible to suppress a change in the opening area of the flow path, and to moderate a change in the damping force that increases when the negative pressure increases. That is, a sudden change in the damping force characteristic of the damper 10 can be suppressed.

FIG. 7 is a diagram showing the damping force characteristics of each damper having different groove shapes. The vertical axis in FIG. 7 indicates the damping force of the damper, and the horizontal axis indicates the pulling speed of the piston. That is, the damping force characteristic of the damper according to the pulling speed of the piston 32 is shown. As the pulling speed of the piston 32 increases, the negative pressure in the first chamber 22 increases. The characteristic 72 of FIG. 7 shows the result of the damper 10 of the embodiment, and the characteristic 70 shows the result of the damper of the comparative example in which the depth of the groove is constant as compared with the damper 10 of the embodiment.

The damper of the comparative example with the characteristic 70 has a constant depth of the groove, so that the outer diameter side of the cover 52 is in contact with the bottom of the groove, but the inner diameter is difficult to contact with the groove. Therefore, although the damping force of the characteristic 70 increases as the pulling speed increases, the degree of change in the damping force is small compared to the characteristic 72 of the damper 10 of the embodiment.

Specifically, until the pulling speed s2, the cover portion 52 enters the groove portion 40, the opening gradually narrows, and both the characteristic 70 and the characteristic 72 greatly change the damping force. In the characteristic 70 of the comparative example, the degree of change of the damping force is greatly different between the pulling speeds s2 to s3 and the pulling speeds s3 to s4, and the degree of change of the damping force is small between the pulling speeds s3 to s4. This is because the inner diameter side of the cover portion 52 cannot contact the groove portion, and the resistance of the flow path becomes almost constant at a pulling speed s3 or more.

On the other hand, in the characteristic 72, the change in the damping force from the pulling speed s2 to s4 is constant, and the degree of change from the pulling speed s3 to s4 is larger than the characteristic 70. This is because the negative pressure in the first chamber 22 increases with an increase in the pulling speed, whereby the cover 52 gradually enters the groove 40 from the outer diameter side to the inner diameter side, and the portion where the opening of the flow path becomes narrower This is because the resistance of the flow path gradually increases because it extends in the radial direction. In this manner, the load responsiveness of the damper 10 is improved by inclining the groove portion 40 so that the depth decreases from the outer region toward the inner region.

8A shows the communication hole 136 and the attachment hole 138 of the first modification, and FIG. 8B shows the communication hole 236 and the attachment hole 38 of the second modification. The communication hole 136 and the attachment hole 138 shown in FIG. A pair of fan-shaped communication holes 136 are connected to each other around a circular mounting hole 138 and formed integrally. By connecting and forming the communication hole 136 and the attachment hole 138 in this way, the opening area of the communication hole 136 can be increased within the range covered by the cover portion 52.

The communication hole 236 shown in FIG. 8B is formed in a C shape across the groove 40. Also in this aspect, the opening area of the communication hole 236 can be increased within the range covered by the cover portion 52. By increasing the opening area of the communication hole, the negative pressure can be efficiently transmitted to the cover portion 52 through the first chamber 22, and the cover portion 52 can be easily bent.

The present invention is not limited to the above-described embodiments, and various modifications such as design changes can be added to the embodiments based on the knowledge of those skilled in the art. Embodiments described may also be included within the scope of the present invention.

In the embodiment, when the piston 32 is pushed, the damping force generated from the damper 10 is small. When the piston 32 is pulled, the damping force generated from the damper 10 is large. However, the present invention is not limited to this mode. . For example, the damper of the modified example covers the communication hole 36 with the cover portion 52 from the first chamber 22 side located on the bottom side of the cylinder 20, and the groove portion 40 is also formed on the back surface of the piston 32 on the first chamber 22 side. Thus, the damper can be configured such that when the piston 32 is pushed, the damping force generated from the damper 10 is large, and when the piston 32 is pulled, the damping force generated from the damper 10 is small.

10 damper, 20 cylinder, 22 1st chamber, 24 2nd chamber, 30 piston rod, 32 piston, 34 rod, 35 lid member, 36 communication hole, 38 mounting hole, 40 groove, 40a corner, 42 ring retaining groove, 44 disc part, 46 cylindrical part, 50 valve, 52 cover part, 54 shaft part, 56 diameter expanding part, 58 step part, 60 seal ring.

Claims

A cylinder,
A piston that is reciprocally inserted into the cylinder, divides the cylinder into a first chamber and a second chamber, and a piston having a communication hole that communicates the first chamber and the second chamber;
A valve attached to the piston,
The valve has a cover portion that covers the communication hole from the second chamber side,
The piston has a groove formed from an inner region covered by the cover part to an outer region outside the cover part,
When the pressure of the first chamber decreases due to the movement of the piston, the cover portion bends into the groove portion and narrows the opening of the flow path in the groove portion,
The damper is characterized in that the groove is formed so as to be inclined so that the depth decreases from the outer region toward the inner region.
The damper according to claim 1, wherein the groove portion is formed so that a groove width becomes narrower from the outer region toward the inner region.
When the cover part is dented by the negative pressure in the first chamber and is bent into the groove part, the cover part leaves a gap in the groove part, and the fluid in the second chamber passes through the gap to the first chamber. The damper according to claim 1, wherein the damper is possible.
The groove is formed to have a rectangular cross section,
When the cover part is dented by the negative pressure in the first chamber and bent into the groove part, the cover part is left in contact with a part of the bottom part of the rectangular cross section of the groove part leaving a gap at both corners of the groove part. The damper according to claim 3, wherein the damper contacts.
The valve has a shaft portion extending from the cover portion,
The piston has a mounting hole into which the valve is mounted by inserting the shaft portion,
The damper according to any one of claims 1 to 4, wherein the communication hole is formed in an arc shape around the mounting hole so as to avoid the groove portion.
The damper according to claim 5, wherein a pair of the communication holes are formed in an arc shape surrounding the mounting hole, and are divided on an extension of the groove portion.