WO2015119156A1 - 緩衝器 - Google Patents

緩衝器 Download PDF

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Publication number
WO2015119156A1
WO2015119156A1 PCT/JP2015/053105 JP2015053105W WO2015119156A1 WO 2015119156 A1 WO2015119156 A1 WO 2015119156A1 JP 2015053105 W JP2015053105 W JP 2015053105W WO 2015119156 A1 WO2015119156 A1 WO 2015119156A1
Authority
WO
WIPO (PCT)
Prior art keywords
press
shock absorber
coil spring
piston
cylinder
Prior art date
Application number
PCT/JP2015/053105
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
宜浩 柴田
功 黒岩
Original Assignee
カヤバ工業株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by カヤバ工業株式会社 filed Critical カヤバ工業株式会社
Publication of WO2015119156A1 publication Critical patent/WO2015119156A1/ja

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G15/00—Resilient suspensions characterised by arrangement, location or type of combined spring and vibration damper, e.g. telescopic type
    • B60G15/02—Resilient suspensions characterised by arrangement, location or type of combined spring and vibration damper, e.g. telescopic type having mechanical spring
    • B60G15/06—Resilient suspensions characterised by arrangement, location or type of combined spring and vibration damper, e.g. telescopic type having mechanical spring and fluid damper
    • B60G15/061—Resilient suspensions characterised by arrangement, location or type of combined spring and vibration damper, e.g. telescopic type having mechanical spring and fluid damper with a coil spring being mounted inside the damper
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G13/00—Resilient suspensions characterised by arrangement, location or type of vibration dampers
    • B60G13/02—Resilient suspensions characterised by arrangement, location or type of vibration dampers having dampers dissipating energy, e.g. frictionally
    • B60G13/06—Resilient suspensions characterised by arrangement, location or type of vibration dampers having dampers dissipating energy, e.g. frictionally of fluid type
    • B60G13/08—Resilient suspensions characterised by arrangement, location or type of vibration dampers having dampers dissipating energy, e.g. frictionally of fluid type hydraulic
    • 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
    • F16F1/00—Springs
    • F16F1/02—Springs made of steel or other material having low internal friction; Wound, torsion, leaf, cup, ring or the like springs, the material of the spring not being relevant
    • F16F1/04—Wound springs
    • F16F1/12—Attachments or mountings
    • F16F1/123—Attachments or mountings characterised by the ends of the spring being specially adapted, e.g. to form an eye for engagement with a radial insert
    • 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
    • F16F9/58—Stroke limiting stops, e.g. arranged on the piston rod outside the cylinder
    • F16F9/585—Stroke limiting stops, e.g. arranged on the piston rod outside the cylinder within the cylinder, in contact with working fluid
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2202/00—Indexing codes relating to the type of spring, damper or actuator
    • B60G2202/20—Type of damper
    • B60G2202/24—Fluid damper

Definitions

  • the present invention relates to a shock absorber.
  • the shock absorber is provided with a rebound spring consisting of a coil spring in which resin cushions are mounted on both ends between a rod guide for sealing the cylinder end and supporting the piston rod and a flange provided at the intermediate portion of the piston rod.
  • a rebound spring consisting of a coil spring in which resin cushions are mounted on both ends between a rod guide for sealing the cylinder end and supporting the piston rod and a flange provided at the intermediate portion of the piston rod.
  • the rebound spring is compressed by the rod guide and the flange that approach each other when the shock absorber is extended, thereby exhibiting a reaction force that suppresses the expansion of the shock absorber. Thereby, the impact at the time of maximum extension of a shock absorber is relieved.
  • the resin cushion has a cylindrical press-fit portion called a holder.
  • the resin cushion is fixed to the coil spring by press-fitting a holder of the resin cushion into the inner periphery at the end of the coil spring.
  • a shock absorber is interposed between a vehicle body and a suspension arm that holds wheels.
  • the stroke amount of the shock absorber is reduced with respect to the vertical displacement of the wheel.
  • An object of the present invention is to provide a shock absorber provided with a rebound spring that can reduce poor press-fitting of a resin cushion into a coil spring.
  • the shock absorber is a cylinder, a piston that is slidably inserted into the cylinder, a movably inserted through the cylinder, and one end connected to the piston.
  • the coil spring is provided with a shock absorber having an inner diameter at one or both of the end winding portions at both ends, and the resin cushion having a press-fit portion that is press-fitted into the inner periphery of the end winding portion.
  • FIG. 1 is a longitudinal sectional view of a shock absorber according to an embodiment of the present invention.
  • FIG. 2 is a partially enlarged longitudinal sectional view of the shock absorber according to the embodiment of the present invention.
  • FIG. 3 is a plan view of a rebound spring of a shock absorber according to a modification of the present invention.
  • FIG. 4A is a partially enlarged longitudinal sectional view of a rebound spring of a shock absorber according to another modification of the present invention.
  • FIG. 4B is a plan view of a rebound spring of a shock absorber according to another modification of the present invention.
  • shock absorber 100 according to an embodiment of the present invention will be described with reference to the accompanying drawings.
  • the shock absorber 100 has a cylinder 1, a piston 2 slidably inserted into the cylinder 1, a movably inserted through the cylinder 1, and one end connected to the piston 2.
  • a piston rod 3 and a rebound spring S attached to the outer periphery of the piston rod 3 are provided.
  • the cylinder 1 has a bottomed cylindrical shape, and an annular rod guide 4 is attached to the upper end in FIG.
  • the rod guide 4 seals the upper end opening of the cylinder 1 and the piston rod 3 is inserted through the inner periphery thereof, and supports the piston rod 3 slidably.
  • the inside of the cylinder 1 is partitioned by a piston 2 into an extension side chamber R1 above the piston 2 in FIG. 1 and a pressure side chamber R2 below the piston 2 in FIG.
  • the extension side chamber R1 and the pressure side chamber R2 are filled with a liquid such as hydraulic oil.
  • the free piston 5 is slidably inserted below the piston 2 in the cylinder 1, and an air chamber G filled with gas is formed below the free piston 5.
  • the piston 2 is provided with a passage 2a communicating the extension side chamber R1 and the pressure side chamber R2, and a damping valve 2b as a damping force generating element provided in the middle of the passage 2a.
  • the expansion chamber R1 When the shock absorber 100 is extended, the expansion chamber R1 is compressed by the piston 2, and the liquid in the expansion chamber R1 passes through the passage 2a and moves to the compression chamber R2. At this time, the damping valve 2b applies resistance to the flow of the liquid to increase the pressure in the expansion side chamber R1, thereby generating a differential pressure between the pressure in the expansion side chamber R1 and the pressure in the compression side chamber R2.
  • the pressure side chamber R2 When the shock absorber 100 is contracted, the pressure side chamber R2 is compressed by the piston 2, and the liquid in the pressure side chamber R2 passes through the passage 2a and moves to the extension side chamber R1. At this time, the damping valve 2b applies resistance to the flow of the liquid to increase the pressure in the pressure side chamber R2, thereby generating a differential pressure between the pressure in the pressure side chamber R2 and the pressure in the extension side chamber R1.
  • the shock absorber 100 compresses the expansion side chamber R1 with the piston 2 to increase the pressure in the expansion side chamber R1, and generates a differential pressure between the pressure in the expansion side chamber R1 and the pressure in the compression side chamber R2. Let Then, when the differential pressure acts on the piston 2, the shock absorber 100 outputs a force that prevents the piston 2 from moving upward in FIG. 1 as a damping force.
  • the shock absorber 100 compresses the pressure side chamber R2 with the piston 2 to increase the pressure in the pressure side chamber R2, and generates a differential pressure between the pressure in the pressure side chamber R2 and the pressure in the extension side chamber R1. Then, when the differential pressure acts on the piston 2, the shock absorber 100 outputs a force that prevents the piston 2 from moving downward in FIG. 1 as a damping force.
  • the shock absorber 100 is a so-called single rod type single cylinder shock absorber.
  • an outer cylinder or a tank is provided outside the cylinder 1, and a reservoir filled with gas and liquid is formed between the outer cylinder and the cylinder 1 or inside the tank, and enters the cylinder 1 with the reservoir.
  • a reverse cylinder type absorber which absorbs the change of the volume of the piston rod 3 currently performed.
  • the damping valve 2b is a throttle that allows both the flow of liquid from the expansion side chamber R1 to the compression side chamber R2 and the flow of liquid from the compression side chamber R2 to the expansion side chamber R1.
  • a plurality of passages 2a are provided in the piston 2, a part of which is provided with a damping valve that allows only the flow of liquid from the extension side chamber R1 to the pressure side chamber R2, and the remaining part extends from the pressure side chamber R2.
  • a damping valve that allows only the flow of liquid toward the side chamber R1 may be provided.
  • the passage 2a and the damping valve 2b can be provided in addition to the piston 2, and may be provided in the piston rod 3 or outside the cylinder 1, for example.
  • the piston rod 3 has the piston 2 attached to the lower end in FIG. 1, and the upper end in FIG. 1 protrudes out of the cylinder 1 through the inner periphery of the rod guide 4.
  • a flange-shaped spring seat 3a is provided on the outer periphery of the piston rod 3 on the lower end side in FIG.
  • the rebound spring S is attached to a coil spring 6 which is disposed on the outer periphery of the piston rod 3 through which the piston rod 3 is inserted, and a spring seat side end which is the lower end of the coil spring 6 in FIG.
  • the coil spring 6 includes an end winding portion 6 a at the spring seat side end and an end winding portion 6 b at the rod guide side end.
  • the resin cushion 7 is formed of a hard resin material. As shown in FIG. 2, the resin cushion 7 has an annular cushion body 7a and an outer diameter smaller than that of the cushion body 7a, and the inner circumference of the cushion body 7a. A cylindrical press-fit portion 7b that rises from the side, a taper portion 7c provided on the outer periphery of the upper end in FIG. 2 of the press-fit portion 7b, and a plurality of convex portions 7d provided on the inner periphery of the cushion body 7a.
  • three convex portions 7 d are provided at equal intervals in the circumferential direction of the resin cushion 7, and abut against the outer periphery of the piston rod 3 inserted in the inner periphery of the resin cushion 7 with a pressing force. . Thereby, the resin cushion 7 is fixed to the outer periphery of the piston rod 3.
  • the cushion body 7a is in contact with the spring seat 3a, and the downward movement in FIG.
  • the number of installation of the convex part 7d should just be three or more, and is arbitrary.
  • the resin cushion 8 is formed of a hard resin material. As shown in FIG. 2, the resin cushion 8 has an annular cushion body 8a and an outer diameter smaller than that of the cushion body 8a, and the inner circumference of the cushion body 8a. A cylindrical press-fit portion 8b suspended from the side, a taper portion 8c provided on the outer periphery of the lower end in FIG. 2 of the press-fit portion 8b, and an annular convex portion provided inwardly on the inner periphery of the cushion body 8a 8d.
  • the inner diameter of the resin cushion 8 is set larger than the outer diameter of the piston rod 3, and the convex portion 8d is in sliding contact with the outer periphery of the piston rod 3 inserted in the inner periphery. That is, the resin cushion 8 is slidable in the axial direction on the outer periphery of the piston rod 3.
  • the convex portion 8d may adopt a structure other than an annular shape, and may have a protruding structure similar to the convex portion 7d of the resin cushion 7, for example.
  • the resin cushion 7 is integrated with the coil spring 6 by press-fitting the press-fitting portion 7b into the inner periphery of the end winding portion 6a of the coil spring 6.
  • the resin cushion 8 is integrated with the coil spring 6 by press-fitting the press-fit portion 8 b into the inner periphery of the end winding portion 6 b of the coil spring 6.
  • the shock absorber 100 compresses the expansion side chamber R1 with the piston 2 to increase the pressure in the expansion side chamber R1, and the difference between the pressure in the expansion side chamber R1 and the pressure in the compression side chamber R2 is as described above.
  • produces the force which prevents the upward movement in FIG. 1 of the piston 2 because the said differential pressure acts on the piston 2.
  • the inner diameter of the end winding portions 6a and 6b of the coil spring 6 is between the end winding portion 6a and the end winding portion 6b, and the spring portion 6c capable of generating a reaction force as a spring of the coil spring 6 is used.
  • the diameter is larger than the inner diameter.
  • the inner diameter of the end turn part 6a is such that when the press-fitting part 7b of the resin cushion 7 is press-fitted into the end turn part 6a, it becomes difficult to insert the press-fitting part 7b due to the tight force with which the end turn part 6a tightens the press-fitting part 7b. It is set so that there is no.
  • the inner diameter of the end turn 6a is smaller than the maximum outer diameter of the press-fit portion 7b of the resin cushion 7, and the press fit allowance (from the maximum outer diameter of the press-fit portion 7b of the resin cushion 7 to the end of the end turn 6a). A value obtained by subtracting the inner diameter).
  • the inner diameter of the end turn part 6a is such that even if the press-fitting part 7b is inserted into the end turn part 6a and the end turn part 6a expands in diameter, the end of the end turn part 6a may scratch the press-fit part 7b or be damaged. Is set to a diameter that does not make it difficult to press-fit the entire press-fit portion 7b.
  • the press-fitting allowance may be determined according to the rigidity of the end winding portion 6a of the coil spring 6.
  • the press-fitting portion 7b of the resin cushion 7 is provided with a taper portion 7c. 6a is gradually expanded in diameter. Thereby, it becomes easy to press-fit the press-fit portion 7b of the resin cushion 7 into the end turn portion 6a.
  • the inner diameter of the end turn 6b is such that when the press-fit portion 8b of the resin cushion 8 is press-fitted into the end turn 6b, it is difficult to insert the press-fit portion 8b due to the tight force with which the end turn 6b tightens the press-fit portion 8b. It is set not to become.
  • the inner diameter of the end turn part 6b is smaller than the maximum outer diameter of the press-fit part 8b of the resin cushion 8, and the press-fitting allowance (from the maximum outer diameter of the press-fit part 8b of the resin cushion 8 to the end part 6b A value obtained by subtracting the inner diameter).
  • the inner diameter of the end turn 6b is such that even if the press-fit portion 8b is inserted into the end turn 6b and the end turn 6b is enlarged, the end of the end turn 6b is damaged by the press-fit portion 8b. Is set to a diameter that does not make it difficult to press-fit the entire press-fitting portion 8b.
  • the press-fitting portion 8b of the resin cushion 8 is provided with a taper portion 8c.
  • the end-fitting portion depends on the degree of insertion of the press-fitting portion 8b. 6b is gradually expanded in diameter. Thereby, it becomes easy to press-fit the press-fit portion 8b of the resin cushion 8 into the end turn portion 6b.
  • the press-fit portions 7b and 8b of the resin cushions 7 and 8 are pressed into the end turns 6a and 6b, respectively. Since it is not caught in the middle or the press-fitting portions 7b and 8b are not damaged, press-fitting failure can be reduced.
  • the rebound spring S can be configured by replacing only the coil spring 6 while using one type of resin cushions 7 and 8 respectively. For this reason, parts management is also easy, the manufacturing cost of the shock absorber 100 can be reduced, and incorrect assembly of the resin cushions 7 and 8 can be prevented.
  • the end winding part 6a , 6b when the end winding parts 6a and 6b are formed in the circumference
  • the half-circumferential portion may be expanded outward so that the curvature gradually decreases from the base T toward the tip U, or bent from the base T,
  • the base T to the tip U may be expanded outward without changing the curvature.
  • the manufacturing cost of the shock absorber 100 is very advantageous. Further, since the end of the end turns 6a, 6b is less likely to come into contact with the press-fit portions 7b, 8b, when the press-fit portions 7b, 8b are press-fit into the end turns 6a, 6b, the end portions of the press-fit portions 7b, 8b are turned. Can be prevented.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Springs (AREA)
  • Fluid-Damping Devices (AREA)
  • Vehicle Body Suspensions (AREA)
PCT/JP2015/053105 2014-02-06 2015-02-04 緩衝器 WO2015119156A1 (ja)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2014021015A JP6128652B2 (ja) 2014-02-06 2014-02-06 緩衝器
JP2014-021015 2014-02-06

Publications (1)

Publication Number Publication Date
WO2015119156A1 true WO2015119156A1 (ja) 2015-08-13

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ID=53777960

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PCT/JP2015/053105 WO2015119156A1 (ja) 2014-02-06 2015-02-04 緩衝器

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JP (1) JP6128652B2 (ru)
WO (1) WO2015119156A1 (ru)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2555615A (en) * 2016-11-04 2018-05-09 Jaguar Land Rover Ltd Shock absorber and vehicle

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2021011902A (ja) * 2019-07-05 2021-02-04 Ｋｙｂ株式会社 緩衝器

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS62196940U (ru) * 1986-06-05 1987-12-15
JPH09291949A (ja) * 1996-04-26 1997-11-11 F C C:Kk クラッチのリターン機構用ばね
JP2004084776A (ja) * 2002-08-27 2004-03-18 Kayaba Ind Co Ltd リバウンドスプリングおよび緩衝器
WO2006129710A1 (ja) * 2005-05-31 2006-12-07 Nhk Spring Co., Ltd. コイルばね

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5543305Y2 (ru) * 1975-03-07 1980-10-11
JPS644235Y2 (ru) * 1979-10-25 1989-02-03

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS62196940U (ru) * 1986-06-05 1987-12-15
JPH09291949A (ja) * 1996-04-26 1997-11-11 F C C:Kk クラッチのリターン機構用ばね
JP2004084776A (ja) * 2002-08-27 2004-03-18 Kayaba Ind Co Ltd リバウンドスプリングおよび緩衝器
WO2006129710A1 (ja) * 2005-05-31 2006-12-07 Nhk Spring Co., Ltd. コイルばね

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2555615A (en) * 2016-11-04 2018-05-09 Jaguar Land Rover Ltd Shock absorber and vehicle

Also Published As

Publication number Publication date
JP6128652B2 (ja) 2017-05-17
JP2015148267A (ja) 2015-08-20

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