WO2014013651A1 - Damper - Google Patents

Damper Download PDF

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Publication number
WO2014013651A1
WO2014013651A1 PCT/JP2013/002863 JP2013002863W WO2014013651A1 WO 2014013651 A1 WO2014013651 A1 WO 2014013651A1 JP 2013002863 W JP2013002863 W JP 2013002863W WO 2014013651 A1 WO2014013651 A1 WO 2014013651A1
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WO
WIPO (PCT)
Prior art keywords
groove
chamber
piston
damper
cover
Prior art date
Application number
PCT/JP2013/002863
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French (fr)
Japanese (ja)
Inventor
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
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Application filed by 株式会社パイオラックス filed Critical 株式会社パイオラックス
Publication of WO2014013651A1 publication Critical patent/WO2014013651A1/en

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/32—Details
    • F16F9/34—Special valve constructions; Shape or construction of throttling passages
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/32—Details
    • F16F9/34—Special valve constructions; Shape or construction of throttling passages
    • F16F9/3415—Special valve constructions; Shape or construction of throttling passages characterised by comprising plastics, elastomeric or porous elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/02—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium using gas only or vacuum
    • F16F9/0209—Telescopic
    • F16F9/0218—Mono-tubular units
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/32—Details

Definitions

  • 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.
  • 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.
  • the present invention has been made in view of such problems, and an object thereof is to provide a damper having improved load response.
  • a damper in order to solve the above-described problems, 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.
  • 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.
  • 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.
  • 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.
  • the load responsiveness of the damper can be improved.
  • FIG. 8A shows the communication hole and the attachment hole of the first modification
  • 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.
  • 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
  • the communication hole is closed and the damping force is increased.
  • 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,
  • FIG. 2 (c) is a view of the piston rod 30 shown in FIG. 2 (b).
  • 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
  • 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.
  • 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
  • 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.
  • 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.
  • 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.
  • 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
  • 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.
  • the cross section of the groove 40 is formed in a rectangular shape.
  • the cover 52 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.
  • the opening of a flow path is securable.
  • 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).
  • 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.
  • 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
  • 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.
  • 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.
  • abuts with the bottom part 40b of the groove part 40 becomes long, the space
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • FIG. 8A shows the communication hole 136 and the attachment hole 138 of the first modification
  • 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 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.
  • 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.
  • the present invention relates to a damper that generates a damping force in accordance with the movement of a piston.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Fluid-Damping Devices (AREA)

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

ダンパーDamper
　本発明は、ピストンの移動に応じて減衰力を生じるダンパーに関する。 The present invention relates to a damper that generates a damping force in accordance with the movement of a piston.
　車両のグローブボックスのふた部材にはダンパーが設けられる。このダンパーによって、ふた部材を開く場合にふた部材がゆるやかに開かれ、閉じる場合にあまり抵抗なく容易に閉じられる。 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.
　たとえば特許文献１には、シリンダと、シリンダに往復可能に挿入されるピストンと、ピストンに軸方向に貫通して形成されたオリフィスと、を備えるエアダンパーが開示される。このエアダンパーは、ピストンの表面に形成されたオリフィス以外の通気路であって、一端がオリフィスに連結され、他端がバルブにより閉止領域外に開放した通気溝を有する。この通気溝は、バルブによってオリフィスが閉じられた場合にオリフィスに通気をして、オリフィスが完全に閉じられたことにより、減衰力が高まりすぎることを抑える。 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.
実開平２－５８１３７号公報Japanese Utility Model Publication No. 2-58137
　特許文献１に記載の技術では、通気溝を形成することでエアダンパーの荷重応答性を向上させているが、通気溝を形成するだけでは荷重応答性の変化は小さく、荷重応答性をいっそう高めたダンパーが望まれている。 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.
　本発明はこのような課題に鑑みてなされたものであり、その目的は、荷重応答性を向上したダンパーを提供することにある。 The present invention has been made in view of such problems, and an object thereof is to provide a damper having improved load response.
　上記課題を解決するために、本発明のある態様のダンパーは、シリンダと、シリンダに往復可能に挿入され、シリンダを第１室と第２室とに仕切り、第１室と第２室とを連通する連通孔が形成されたピストンと、連通孔に取り付けられるバルブと、を備える。バルブは、連通孔を第２室側から覆うカバー部を有する。ピストンは、カバー部により覆われた内部領域からカバー部の外側の外部領域に亘って形成された溝部を有する。カバー部は、ピストンの移動により第１室の圧力が低下すると、溝部内に撓んで溝部における流路の開口を狭め、溝部は、外部領域から内部領域に向かって深さが浅くなるように傾斜して形成される。 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.
　この態様によると、第１室の負圧によってカバー部が溝部に入り込むことで、流路の開口面積を変化させることができる。また、溝部は外部領域から内部領域に向かって深さが浅くなるように傾斜して形成されることで、撓みにくいカバー部内径側が溝部へ吸い込まれる量が少なくても、外径側の流路の開口面積と同様に開口面積を狭めることができる。これによって、第１室の負圧が強くなるにつれて、カバー部の内径側が溝部に徐々に入り込み、流路の開口面積の狭まりが外径から内径側に連続することにより、流路の抵抗を徐々に高め、荷重応答性を向上することができる。 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.
　本発明によれば、ダンパーの荷重応答性を向上することができる。 According to the present invention, the load responsiveness of the damper can be improved.
実施形態に係るダンパーの斜視図である。It is a perspective view of the damper concerning an embodiment. ピストンロッドを説明するための図である。It is a figure for demonstrating a piston rod. バルブを説明するための図である。It is a figure for demonstrating a valve | bulb. ピストンとバルブの位置関係を説明するための図である。It is a figure for demonstrating the positional relationship of a piston and a valve | bulb. 第１室の負圧が相対的に弱い場合のバルブの溝部への作用を説明するための図である。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. 第１室の負圧が相対的に強い場合のバルブの溝部への作用を説明するための図である。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. 異なる溝部の形状を有するそれぞれのダンパーの減衰力特性を示す図である。It is a figure which shows the damping-force characteristic of each damper which has a shape of a different groove part. 図８（ａ）は、第１変形例の連通孔および取付孔を示し、図８（ｂ）は、第２変形例の連通孔および取付孔を示す。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.
　図１は、実施形態に係るダンパー１０の斜視図である。ダンパー１０は、たとえば車両のグローブボックスに取り付けられ、グローブボックスの開閉部材（ふた部材）の開閉に減衰力を付与する。ダンパー１０は、シリンダ２０、ピストンロッド３０、バルブ５０およびシールリング６０を備える。 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.
　シリンダ２０は、有底の円筒形状に形成される。シリンダ２０には、ピストンロッド３０が挿入される。ピストンロッド３０は、シリンダ２０内を仕切るピストン３２と、ロッド３４を有する。ピストン３２によりシリンダ２０内に第１室２２と第２室２４が形成される。ピストン３２の外周にはシールリング６０が設けられ、第１室２２の密閉度合いが向上される。なお、第２室２４は外気に開放されていてよい。 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.
　ロッド３４は、一端がピストン３２に固定され、他端が開閉部材に直接または間接に連結される。ピストン３２は、シリンダ２０に挿入され、開閉部材の動作に応じて往復する。バルブ５０は、ピストン３２に取り付けられ、ピストン３２に形成された連通孔（不図示）を第２室２４側から覆う。バルブ５０は、気体が第１室２２から第２室２４に出る場合に連通孔を開き、気体が第２室２４から第１室２２に入る場合に連通孔を閉じるよう動作する。つまり、ダンパー１０は、ピストン３２が押されて第１室２２の圧力が高まると第１室２２の気体を連通孔から放出して減衰力を抑え、ピストン３２が引かれて第１室２２の圧力が低くなると連通孔を閉じ、減衰力を高める。グローブボックスにおいては、ふた部材を開くときはピストン３２が引かれてゆっくり開き、ふた部材を閉じるときはピストン３２が押されて容易に閉じられる。 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.
　図２は、ピストンロッド３０を説明するための図である。図２（ａ）は、ピストンロッド３０の斜視図であり、図２（ｂ）は、ピストンロッド３０の正面図であり、図２（ｃ）は、図２（ｂ）に示すピストンロッド３０の線分Ａ－Ａの断面図である。ここで各図面に示される同一または同等の構成要素、部材には、同一の符号を付するものとし、適宜重複した説明は省略する。 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.
　ピストン３２は、カップ状に形成され、円盤部４４と、円盤部４４の外周に設けられた円筒部４６とを有する。円盤部４４の表面にロッド３４が設けられる。なお、円盤部４４の表面は外部に露出し、裏面は第１室２２を形成する。円筒部４６の外周にシールリング６０を保持するためのリング保持溝４２が形成される。 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.
　円盤部４４は、第１室２２と第２室２４を連通する連通孔３６、バルブ５０が取り付けられる取付孔３８および溝部４０を有する。溝部４０は円盤部４４の表面に形成される。円盤部４４の表面は、第２室２４側の面である。図２（ｂ）に示すように溝部４０は、連通孔３６および取付孔３８の周囲から径方向外向きに延在する。 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.
　連通孔３６および取付孔３８は、円盤部４４を貫通して第１室２２および第２室２４を連通する。連通孔３６は取付孔３８の周囲に形成される。溝部４０と連通孔３６および取付孔３８は離間する。 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.
　図３は、バルブ５０を説明するための図である。図３（ａ）は、バルブ５０の側面図であり、図３（ｂ）は、ピストン３２に取り付けた状態のバルブ５０の断面図である。バルブ５０は、カバー部５２と軸部５４と拡径部５６と段部５８を有する。バルブ５０は、傘形状に形成される。 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.
　カバー部５２は、可撓性を有し、軸部５４から径方向外向きに垂下する円形に形成される。カバー部５２の裏面の中央に軸部５４が形成される。軸部５４の中途にて拡径する拡径部５６が形成される。カバー部５２は、連通孔３６を第２室２４側から覆う。 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.
　図３（ｂ）に示すように軸部５４は、カバー部５２から第１室２２に向かって延出する。軸部５４は取付孔３８に挿入され、拡径部５６により抜け止めされている。軸部５４の根元に形成された段部５８は、負圧によりカバー部５２が吸引された場合に、軸部５４が軸方向に移動しすぎないように制限する。 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.
　カバー部５２の外周はピストン３２の表面に接触する。カバー部５２の外周より内側をピストン３２の表面の内部領域といい、カバー部５２の外周より外側を外部領域という。
連通孔３６は内部領域の中に位置する。カバー部５２は、連通孔３６から負圧を受けると凹み、正圧を受けると浮き上がって空気を逃がす。 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.
　図４は、ピストン３２とバルブ５０の位置関係を説明するための図である。図４（ａ）は、バルブ５０の取付位置近傍を示すピストン３２の斜視図であり、図４（ｂ）は、ピストン３２に取り付けた状態のバルブ５０を示す斜視図である。 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.
　連通孔３６は、取付孔３８の周囲において溝部４０を避けて径方向断面が円弧状に形成される。連通孔３６は取付孔３８を中心として取付孔３８を囲うように形成される。これにより、カバー部５２に覆われた内部領域の範囲内で取付孔３８の周囲に連通孔３６を大きく形成することができ、負圧をカバー部５２に伝達しやすくできる。また、空気が通過する際に連通孔３６から異音が発生しないよう連通孔３６の大きさを確保できる。連通孔３６が溝部４０を避けることで、連通孔３６と溝部４０が離間する。 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.
　連通孔３６は、取付孔３８を囲んで円弧状に一対形成され、溝部４０の延長上で分断される。連通孔３６を一対設けることで、円筒形状の取付孔３８の縁を２箇所で支持することができ取付孔３８の剛性を向上させることができる。 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.
　図４（ｂ）に示すように、取付孔３８にバルブ５０を取り付けると、連通孔３６は全てカバー部５２に覆われる。すなわち、カバー部５２の外径は、一対の連通孔３６の外径より大きくなるように形成される。溝部４０は、カバー部５２により覆われた内部領域からカバー部５２の外側の外部領域に亘って形成される。これにより、内部領域と外部領域を連通し、気体の流路が形成される。 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.
　図４（ｂ）では、第１室２２の負圧によりカバー部５２が凹むよう撓んだ状態を示す。溝部４０にカバー部５２が入り込み、溝部４０の流路の開口が狭められている。溝部４０にカバー部５２が入り込むものの、溝部４０の角部４０ａにカバー部５２は非接触であり、溝部４０の流路の開口の一部は開放される。すなわち、カバー部５２が溝部４０に入り込んでも隙間が残り、その隙間から第２室２４の流体が第１室２２に通過可能である。このように気体の流路を確保できる。 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.
　ダンパー１０は、ピストン３２の移動により第１室２２の負圧が強くなるほど、溝部４０にカバー部５２が入り込み、流路の開口が狭められるので、大きな減衰力を発生する。このように溝部４０を形成することで、溝部４０がなくピストン３２の表面が平らである場合と比べて、溝部４０の流路の開口面積を調整することができる。 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.
　図５は、第１室２２の負圧が相対的に弱い場合のバルブ５０の溝部４０への作用を説明するための図である。図５（ａ）は、ピストン３２およびバルブ５０の部分断面図であり、図５（ｂ）は、図５（ａ）に示すピストン３２およびバルブ５０の線分Ｂ－Ｂの断面図であり、図５（ｃ）は、図５（ａ）に示すピストン３２およびバルブ５０の線分Ｃ－Ｃの断面図である。 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.
　図５（ｂ）および図５（ｃ）に示すように溝部４０の断面は矩形に形成される。図５（ｂ）に示すように、第１室２２の負圧によりカバー部５２が凹んで溝部４０に撓んだ場合、カバー部５２は、溝部４０の底部の両角部４０ａに隙間を残して溝部４０の矩形断面の底部の一部に当接する。このように複数の角部４０ａを設けることで、流路の開口を確保することができる。 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.
　図５（ａ）に示すように、第１室の負圧が弱いため、カバー部５２は最外径端部だけ溝部４０に入り込む。図５（ｂ）に示すカバー部５２の外径側は溝部４０の底部に当接する一方で、図５（ｃ）に示すカバー部５２の内径側は溝部４０に接触しない。これは、バルブ５０の外径側は撓みやすく、内径側は撓みにくいためである。 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.
　図５（ｂ）に示す外径側の溝部４０より図５（ｃ）に示す内径側の溝部４０の方が深さが浅く、溝幅が狭くなるように形成されている。具体的には、溝部４０の底部４０ｂは滑らかな傾斜面であり、径方向内向きに溝部４０の深さが浅くなるように傾斜して形成される。カバー部５２との関係では、外部領域から内部領域に向かって溝部４０の深さが浅くなる。これにより、撓みにくいカバー部５２の内径側が、溝部４０に当接しやすくなる。 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.
　図６は、第１室２２の負圧が相対的に強い場合のバルブ５０の溝部４０への作用を説明するための図である。図６（ａ）は、ピストン３２およびバルブ５０の部分断面図であり、図６（ｂ）は、図６（ａ）に示すピストン３２およびバルブ５０の線分Ｄ－Ｄの断面図であり、図６（ｃ）は、図６（ａ）に示すピストン３２およびバルブ５０の線分Ｅ－Ｅの断面図である。 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.
　図６（ａ）に示す第１室２２での負圧は、図５（ａ）に示す態様より強く、カバー部５２は大きく撓む。そのためカバー部５２は最外径から内径側へ所定間隔に亘って溝部４０に当接する。これは、溝部４０の深さが径方向内向きに浅くなるように形成されているため、カバー部５２の内径側が溝部４０に当接しやくなっているからである。 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.
　図６（ｂ）および図６（ｃ）に示すようにカバー部５２の最外径端部および内径側において溝部４０の底部４０ｂに当接する。ここで、カバー部５２が溝部４０の底部４０ｂと当接する間隔が長くなれば、狭まった流路の間隔が長くなって移動抵抗が大きくなり、気体が通りにくくなる。したがって、第１室２２の負圧が強くなるにつれて、気体が通りにくくなり、ダンパー１０における減衰力を高めることができる。 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.
　溝部４０は、ピストン３２表面の外部領域から内部領域に向かって、すなわち径方向内向きに溝幅が狭くなるように形成される。溝部４０が浅くなった箇所において、底部４０ｂ全体にカバー部５２が張り付くことを抑えることができ、流路の開口を確保することができる。また、流路の開口を確保することで、流路の開口面積の変化を抑えることができ、負圧が強まった場合に高まる減衰力の変化を緩やかにできる。すなわちダンパー１０の減衰力特性が急激に変化することを抑えることができる。 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.
　図７は、異なる溝部の形状を有するそれぞれのダンパーの減衰力特性を示す図である。図７の縦軸はダンパーの減衰力を示し、横軸は、ピストンの引っ張り速度を示す。つまり、ピストン３２の引っ張り速度に応じたダンパーの減衰力特性を示している。ピストン３２の引っ張り速度が高くなるにつれて第１室２２の負圧が大きくなる。図７の特性７２は、実施形態のダンパー１０の結果を示し、特性７０は、実施形態のダンパー１０と比べて溝部の深さが一定である比較例のダンパーの結果を示す。 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.
　特性７０の比較例のダンパーは、溝部の深さが一定なので、カバー部５２の外径側は溝部の底部に当接するものの内径側は溝部に当接しづらい。したがって特性７０は引っ張り速度が大きくなれば減衰力は高くなるものの、実施形態のダンパー１０の特性７２と比べると、減衰力の変化の度合いは少ない。 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.
　具体的に、引っ張り速度ｓ２までは、溝部４０にカバー部５２が入り込んで開口が徐々に狭くなって特性７０および特性７２ともに減衰力が大きく変化する。比較例の特性７０において、引っ張り速度ｓ２からｓ３と引っ張り速度ｓ３からｓ４の間では、減衰力の変化度合いが大きく異なり、引っ張り速度ｓ３からｓ４では減衰力の変化度合いが少ない。これは、カバー部５２の内径側が溝部に当接できず、引っ張り速度ｓ３以上では流路の抵抗がほとんど一定になるためである。 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.
　一方、特性７２において引っ張り速度ｓ２からｓ４までの減衰力の変化は一定で、引っ張り速度ｓ３からｓ４までの変化度合いは特性７０より大きい。これは、引っ張り速度の増加とともに第１室２２の負圧が高まり、それによりカバー部５２が外径側から内径側に亘って徐々に溝部４０に入り、流路の開口が狭くなった部分が径方向に伸びていくため、流路の抵抗が徐々に高くなるためである。このように、溝部４０を外部領域から内部領域に向かって深さが浅くなるように傾斜させることで、ダンパー１０の荷重応答性が向上する。 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.
　図８（ａ）は、第１変形例の連通孔１３６および取付孔１３８を示し、図８（ｂ）は、第２変形例の連通孔２３６および取付孔３８を示す。図８（ａ）に示す連通孔１３６および取付孔１３８は連結される。円形の取付孔１３８を中心に一対の扇形の連通孔１３６が連結し、一体に形成される。このように連通孔１３６および取付孔１３８を連結して形成することで、カバー部５２に覆われる範囲内にて連通孔１３６の開口面積を大きくすることができる。 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.
　図８（ｂ）に示す連通孔２３６は、溝部４０を跨いでＣ字状に形成される。この態様においてもカバー部５２に覆われる範囲内にて連通孔２３６の開口面積を大きくすることができる。連通孔の開口面積を大きくすることで、第１室２２を負圧をカバー部５２に効率的に伝達することができ、カバー部５２を撓みやすくできる。 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.
　本発明は上述の各実施例に限定されるものではなく、当業者の知識に基づいて各種の設計変更等の変形を各実施例に対して加えることも可能であり、そのような変形が加えられた実施例も本発明の範囲に含まれうる。 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.
　実施形態では、ピストン３２を押す場合、ダンパー１０から発生する減衰力は小さく、ピストン３２を引く場合、ダンパー１０から発生する減衰力は大きくなるように構成されているが、この態様に限られない。たとえば、変形例のダンパーは、シリンダ２０の底部側に位置する第１室２２側からカバー部５２で連通孔３６を覆い、溝部４０も第１室２２側のピストン３２の裏面に形成される。これにより、ピストン３２を押す場合、ダンパー１０から発生する減衰力は大きく、ピストン３２を引く場合、ダンパー１０から発生する減衰力は小さくなるようにダンパーを構成できる。 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　ダンパー、　２０　シリンダ、　２２　第１室、　２４　第２室、　３０　ピストンロッド、　３２　ピストン、　３４　ロッド、　３５　蓋部材、　３６　連通孔、　３８　取付孔、　４０　溝部、　４０ａ　角部、　４２　リング保持溝、　４４　円盤部、　４６　円筒部、　５０　バルブ、　５２　カバー部、　５４　軸部、　５６　拡径部、　５８　段部、　６０　シールリング。 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.
　本発明は、ピストンの移動に応じて減衰力を生じるダンパーに関する。 The present invention relates to a damper that generates a damping force in accordance with the movement of a piston.

Claims (6)

  1. 　シリンダと、
    　前記シリンダに往復可能に挿入され、前記シリンダを第１室と第２室とに仕切り、前記第１室と前記第２室とを連通する連通孔が形成されたピストンと、
    　前記ピストンに取り付けられるバルブと、を備え、
    　前記バルブは、前記連通孔を前記第２室側から覆うカバー部を有し、
    　前記ピストンは、前記カバー部により覆われた内部領域から前記カバー部の外側の外部領域に亘って形成された溝部を有し、
    　前記カバー部は、前記ピストンの移動により前記第１室の圧力が低下すると、前記溝部内に撓んで前記溝部における流路の開口を狭め、
    　前記溝部は、前記外部領域から前記内部領域に向かって深さが浅くなるように傾斜して形成されることを特徴とするダンパー。     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.
  2. 　前記溝部は、前記外部領域から前記内部領域に向かって溝幅が狭くなるように形成されることを特徴とする請求項１に記載のダンパー。 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.
  3. 　前記第１室の負圧により前記カバー部が凹んで前記溝部に撓んだ場合、前記カバー部は、前記溝部に隙間を残し、その隙間から前記第２室の流体が前記第１室に通過可能であることを特徴とする請求項１または２に記載のダンパー。 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.
  4. 　前記溝部は、断面が矩形になるよう形成され、
    　前記第１室の負圧により前記カバー部が凹んで前記溝部に撓んだ場合、前記カバー部は、前記溝部の底部の両角に隙間を残して前記溝部の矩形断面の底部の一部に当接することを特徴とする請求項３に記載のダンパー。     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.
  5. 　前記バルブは、前記カバー部から延出する軸部を有し、
    　前記ピストンは、前記軸部を挿入して前記バルブが取り付けられる取付孔を有し、
    　前記連通孔は、前記取付孔の周囲において前記溝部を避けて円弧状に形成されることを特徴とする請求項１から４のいずれかに記載のダンパー。     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.
  6. 　前記連通孔は、前記取付孔を囲んで円弧状に一対形成され、前記溝部の延長上で分断されることを特徴とする請求項５に記載のダンパー。 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.
PCT/JP2013/002863 2012-07-16 2013-04-26 Damper WO2014013651A1 (en)

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102017114475A1 (en) * 2017-06-29 2019-01-03 Druck- und Spritzgußwerk Hettich GmbH & Co. KG damper

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS61282634A (en) * 1985-06-10 1986-12-12 Kiyousan Denki Kk Dash pot
JPH0258137U (en) * 1988-10-24 1990-04-26
JPH0678641U (en) * 1993-04-15 1994-11-04 エヌオーケー株式会社 Piston and damper using it

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS61282634A (en) * 1985-06-10 1986-12-12 Kiyousan Denki Kk Dash pot
JPH0258137U (en) * 1988-10-24 1990-04-26
JPH0678641U (en) * 1993-04-15 1994-11-04 エヌオーケー株式会社 Piston and damper using it

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102017114475A1 (en) * 2017-06-29 2019-01-03 Druck- und Spritzgußwerk Hettich GmbH & Co. KG damper
US11230869B2 (en) 2017-06-29 2022-01-25 Druck- Und Spritzgusswerk Hettich GmbH & Co. KG Damper

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