JP2008175349A - Strut bearing - Google Patents

Strut bearing Download PDF

Info

Publication number
JP2008175349A
JP2008175349A JP2007011389A JP2007011389A JP2008175349A JP 2008175349 A JP2008175349 A JP 2008175349A JP 2007011389 A JP2007011389 A JP 2007011389A JP 2007011389 A JP2007011389 A JP 2007011389A JP 2008175349 A JP2008175349 A JP 2008175349A
Authority
JP
Japan
Prior art keywords
outer ring
inner ring
strut
sliding body
spring seat
Prior art date
Legal status (The legal status 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 status listed.)
Pending
Application number
JP2007011389A
Other languages
Japanese (ja)
Inventor
Tomomasa Kubo
智将 久保
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
JTEKT Corp
Original Assignee
JTEKT Corp
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 JTEKT Corp filed Critical JTEKT Corp
Priority to JP2007011389A priority Critical patent/JP2008175349A/en
Publication of JP2008175349A publication Critical patent/JP2008175349A/en
Pending legal-status Critical Current

Links

Images

Classifications

    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/10—Sliding-contact bearings for exclusively rotary movement for both radial and axial load
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/12—Sliding-contact bearings for exclusively rotary movement characterised by features not related to the direction of the load
    • F16C17/18—Sliding-contact bearings for exclusively rotary movement characterised by features not related to the direction of the load with floating brasses or brushing, rotatable at a reduced speed
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—Sealings
    • F16C33/74—Sealings of sliding-contact bearings
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2326/00—Articles relating to transporting
    • F16C2326/01—Parts of vehicles in general
    • F16C2326/05—Vehicle suspensions, e.g. bearings, pivots or connecting rods used therein
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2361/00—Apparatus or articles in engineering in general
    • F16C2361/53—Spring-damper, e.g. gas springs

Landscapes

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

Abstract

<P>PROBLEM TO BE SOLVED: To easily constitute a strut bearing that can be loaded with a lateral load. <P>SOLUTION: The strut bearing 20 comprises an outer ring 21 fixed to an upper support, and an inner ring 22 fixed to an upper spring seat. The outer ring 21 comprises a raceway surface 21a having a normal L2 intersecting a strut axial line L1. The inner ring 22 comprises a raceway surface 22a having a normal L3 intersecting the strut axial line L1. A sliding body 23 is arranged between the outer ring 21 and the inner ring 22. The sliding body 23 has an inclined surface 23a that can come in face contact with the raceway surface 21a of the outer ring 21, and an inclined surface 23b that can come in face contact with the raceway surface 22a of the inner ring 22. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

本発明は、自動車等の車両に用いられるストラット軸受に関する。   The present invention relates to a strut bearing used in a vehicle such as an automobile.

この種のストラット軸受は、例えば下記特許文献１に記載されているように、車体に取り付けられるアッパーサポートと、ストラットに取り付けられるアッパースプリングシート間に介装されていて、アッパースプリングシートのアッパーサポートに対するストラット軸線回りの回転を許容するように構成されている。この特許文献１に記載されたストラット軸受は、アッパーサポートに固定された外輪と、アッパースプリングシートに固定された内輪とを備えており、その外輪と内輪間には、円板状の摺動体が配置されている。そして、この特許文献１に記載されたストラット軸受では、アッパースプリングシートのアッパーサポートに対するストラット軸線回りの回転時に、摺動体が外輪に対して摺動するようになっている。
実開平７−２９３２１号公報 This type of strut bearing is interposed between an upper support attached to a vehicle body and an upper spring seat attached to the strut, as described in, for example, Patent Document 1 below, and is provided for the upper support of the upper spring seat. It is configured to allow rotation around the strut axis. The strut bearing described in Patent Document 1 includes an outer ring fixed to an upper support and an inner ring fixed to an upper spring seat, and a disc-shaped sliding body is interposed between the outer ring and the inner ring. Is arranged. And in the strut bearing described in this patent document 1, a sliding body slides with respect to an outer ring | wheel at the time of the periphery of the strut axis line with respect to the upper support of an upper spring seat.
Japanese Utility Model Publication No. 7-29321

上記特許文献１に記載されたストラット軸受では、玉、ころ等の転動体を使用するタイプのストラット軸受に比して、一般に軸受の厚みを小さく設定できるので、ストラット軸受が小形になって、ストラット上部と車両のボンネット間のスペースを広げることが可能である。しかしながら、この特許文献１に記載されたストラット軸受では、摺動体が円板状に形成されているので、ストラット軸方向の荷重は負荷できるものの、ストラット軸に直交する横荷重は負荷できない。このため、ストラットを構成するショクアブソーバのピストンロッドに過大な横荷重が負荷されるおそれがある。   In the strut bearing described in Patent Document 1, the thickness of the bearing can be generally set smaller than that of a type of strut bearing that uses rolling elements such as balls and rollers. It is possible to increase the space between the upper part and the hood of the vehicle. However, in the strut bearing described in Patent Document 1, since the sliding body is formed in a disc shape, a load in the strut axis direction can be applied, but a lateral load orthogonal to the strut axis cannot be applied. For this reason, an excessive lateral load may be applied to the piston rod of the shock absorber constituting the strut.

本発明の課題は、横荷重を負荷することが可能なストラット軸受を簡易に構成することにある。   An object of the present invention is to simply configure a strut bearing capable of applying a lateral load.

課題を解決するための手段および発明の効果Means for Solving the Problems and Effects of the Invention

上記課題を解決するために本発明は、
車体に取り付けられるアッパーサポートと、ストラットに取り付けられるアッパースプリングシート間に介装され、前記アッパースプリングシートの前記アッパーサポートに対するストラット軸線回りの回転を許容するストラット軸受において、
前記アッパーサポートに固定された外輪と、
前記アッパースプリングシートに固定された内輪とを備え、
前記外輪と前記内輪間には、前記外輪の軌道面との接触面および前記内輪の軌道面との接触面のうちの少なくとも一方の接触面の法線が前記ストラット軸線と交差する傾斜面に形成された環状の摺動体が配置されていることを特徴とする。この場合、例えば、前記摺動体の傾斜面は、径方向外方に向かうに従って厚みが増加するように傾斜方向が設定されるように構成するとよい。 In order to solve the above problems, the present invention
In a strut bearing interposed between an upper support attached to a vehicle body and an upper spring seat attached to a strut and allowing rotation of the upper spring seat around the strut axis with respect to the upper support.
An outer ring fixed to the upper support;
An inner ring fixed to the upper spring seat,
Between the outer ring and the inner ring, a normal line of at least one of a contact surface with the raceway surface of the outer ring and a contact surface with the raceway surface of the inner ring is formed on an inclined surface intersecting the strut axis. An annular sliding body is arranged, which is characterized in that it is arranged. In this case, for example, the inclined surface of the sliding body may be configured such that the inclined direction is set so that the thickness increases as it goes radially outward.

本発明のストラット軸受においては、摺動体の少なくとも一方の接触面の法線がストラット軸線と交差する傾斜面に形成されている。このため、アッパースプリングシートを経て内輪に横荷重が作用した場合には、楔の原理により摺動体から外輪に対してストラット軸方向の荷重が作用し、この荷重は外輪からアッパーサポートを経て車体に作用するので、横荷重を負荷することが可能となる。   In the strut bearing of the present invention, the normal line of at least one contact surface of the sliding body is formed on an inclined surface intersecting the strut axis. For this reason, when a lateral load acts on the inner ring via the upper spring seat, a load in the strut axial direction acts on the outer ring from the sliding body by the wedge principle, and this load is applied to the vehicle body from the outer ring via the upper support. Since it acts, it becomes possible to apply a lateral load.

また、本発明の実施に際して、前記内輪、前記外輪および前記摺動体は樹脂で形成され、前記内輪と前記外輪との両軌道面または前記摺動体の両接触面には、油溜め用の凹部が形成されていることも可能である。これによれば、凹部内に潤滑油が溜められるので、アッパースプリングシートのアッパーサポートに対するストラット軸線回りの回転時において、内外輪と摺動体間の摩擦抵抗を効果的に低減することが可能である。   In carrying out the present invention, the inner ring, the outer ring, and the sliding body are formed of resin, and recesses for oil sumps are formed on both raceway surfaces of the inner ring and the outer ring or on both contact surfaces of the sliding body. It can also be formed. According to this, since the lubricating oil is stored in the recess, it is possible to effectively reduce the frictional resistance between the inner and outer rings and the sliding body when rotating around the strut axis with respect to the upper support of the upper spring seat. .

また、本発明の実施に際して、前記外輪および前記内輪は、前記摺動体を介在させた状態で互いに係合して前記外輪と前記内輪とを一体的に結合する係合部を備えてなることも可能である。これによれば、係合部同士の係合により外輪、内輪および摺動体の組み付けが容易となって、組み付け後に分離（ばらけ）し難い構造とすることが可能である。また、ラビリンス効果により防塵効果が良好となり、内部に封入された潤滑油の外部への漏れを効果的に防止することも可能である。   In carrying out the present invention, the outer ring and the inner ring may include an engaging portion that engages with each other with the sliding body interposed therebetween to integrally couple the outer ring and the inner ring. Is possible. According to this, the outer ring, the inner ring, and the sliding body can be easily assembled by the engagement of the engaging portions, and a structure that is difficult to separate (separate) after the assembly can be obtained. In addition, the labyrinth effect provides a good dustproof effect, and it is possible to effectively prevent leakage of the lubricating oil enclosed inside to the outside.

（第１実施形態）
以下、本発明の第１実施形態を図面に基づいて説明する。図１は、本発明の第１実施形態に係るストラット軸受を採用したストラット上部を概略的に示していて、このストラットは、ショックアブソーバ１１、コイルスプリング１２およびアッパーサポート１３を備えている。 (First embodiment)
DESCRIPTION OF EXEMPLARY EMBODIMENTS Hereinafter, a first embodiment of the invention will be described with reference to the drawings. FIG. 1 schematically shows an upper portion of a strut that employs a strut bearing according to a first embodiment of the present invention. This strut includes a shock absorber 11, a coil spring 12, and an upper support 13.

ショックアブソーバ１１は、ピストンロッド１１ａの先端部にてアッパーサポート１３を介して車体ＢＤに固定されている。コイルスプリング１２は、シリンダ１１ｂに固定されたロアスプリングシート（図示省略）とアッパースプリングシート１４間に介装されている。   The shock absorber 11 is fixed to the vehicle body BD via the upper support 13 at the tip of the piston rod 11a. The coil spring 12 is interposed between a lower spring seat (not shown) fixed to the cylinder 11 b and an upper spring seat 14.

アッパーサポート１３は、ゴム等の弾性体１３ａと、弾性体１３ａの上面および側面に固着された外筒部材１３ｂと、弾性体１３ａの下面に固着された底板部材１３ｃとで構成されている。この底板部材１３ｃの下面とアッパースプリングシート１４の上面間には、ストラット軸受（以下、単に軸受ともいう）２０が取り付けられている。   The upper support 13 includes an elastic body 13a such as rubber, an outer cylinder member 13b fixed to the upper surface and side surfaces of the elastic body 13a, and a bottom plate member 13c fixed to the lower surface of the elastic body 13a. A strut bearing (hereinafter also simply referred to as a bearing) 20 is attached between the lower surface of the bottom plate member 13 c and the upper surface of the upper spring seat 14.

軸受２０は、図２および図３に示すように、アッパースプリングシート１４のアッパーサポート１３に対するストラット軸線Ｌ１回りの回転を許容スラストタイプのものであり、外輪２１、内輪２２および摺動体２３を備えている。   2 and 3, the bearing 20 is of a thrust type that allows the upper spring seat 14 to rotate around the strut axis L1 relative to the upper support 13, and includes an outer ring 21, an inner ring 22, and a sliding body 23. Yes.

外輪２１は、円環状の樹脂成形品であり、アッパーサポート１３の底板部材１３ｃの下面に固定されていて、その内側部には摺動体２３と面接触可能な軌道面２１ａが形成されている。軌道面２１ａは、その法線Ｌ２が車両上方に向かうに従ってストラット軸線Ｌ１に接近するような傾斜面に形成されている。軌道面２１ａの径方向外縁には、摺動体２３の上部外周端を位置決めするための段部２１ｂが形成されている。また、外輪２１の内側部には、小内径位置に車両下方に向けて円環状かつ爪形状の係合部２１ｃが突設され、大内径位置に車両下方に向けて円環状かつ爪形状の係合部２１ｄが突設されている。   The outer ring 21 is an annular resin molded product, and is fixed to the lower surface of the bottom plate member 13 c of the upper support 13. A raceway surface 21 a that can come into surface contact with the sliding body 23 is formed on the inner side thereof. The raceway surface 21a is formed in an inclined surface that approaches the strut axis L1 as its normal line L2 goes upward in the vehicle. A step portion 21b for positioning the upper outer peripheral end of the sliding body 23 is formed on the outer circumferential edge of the raceway surface 21a. Further, an annular and claw-shaped engagement portion 21c is projected from the inner side of the outer ring 21 toward the lower side of the vehicle at a small inner diameter position, and an annular and claw-shaped engagement at the larger inner diameter position toward the lower side of the vehicle. A joint portion 21d is projected.

内輪２２は、円環状の樹脂成形品であり、アッパースプリングシート１４の上面に固定されていて、その内側部には摺動体２３と面接触可能な軌道面２２ａが形成されている。軌道面２２ａは、その法線Ｌ３が車両下方に向かうに従ってストラット軸線Ｌ１に接近するような傾斜面に形成されている。軌道面２２ａの径方向外縁には、摺動体２３の下部外周端を位置決めするための段部２２ｂが形成されている。また、内輪２２の内側部には、小内径位置に車両上方に向けて円環状かつ爪形状の係合部２２ｃが突設され、大内径位置に車両上方に向けて円環状かつ爪形状の係合部２２ｄが突設されている。   The inner ring 22 is an annular resin molded product, and is fixed to the upper surface of the upper spring seat 14, and a raceway surface 22 a that can come into surface contact with the sliding body 23 is formed on the inner side thereof. The track surface 22a is formed in an inclined surface such that the normal line L3 approaches the strut axis L1 as it goes downward of the vehicle. A step portion 22b for positioning the lower outer peripheral end of the sliding body 23 is formed on the outer circumferential edge of the raceway surface 22a. Further, an annular and claw-shaped engaging portion 22c is projected from the inner side of the inner ring 22 toward the upper side of the vehicle at a small inner diameter position, and an annular and claw-shaped engagement at the larger inner diameter position toward the upper side of the vehicle. A joint portion 22d is projected.

摺動体２３は、円環状の樹脂成形品（テーパ状ブッシュ）であり、その上面にて外輪２１の軌道面２１ａと面接触可能な傾斜面２３ａを有し、その下面にて内輪２２の軌道面２２ａと面接触可能な傾斜面２３ｂを有する断面台形状に形成されている。摺動体２３の傾斜面２３ａの中間部位には、潤滑油を溜めるための凹部２３ａ１が全周に渡って形成され、摺動体２３の傾斜面２３ｂの中間部位には、潤滑油を溜めるための凹部２３ｂ１が全周に渡って形成されている。   The sliding body 23 is an annular resin molded product (tapered bush), and has an inclined surface 23a that can come into surface contact with the raceway surface 21a of the outer ring 21 on its upper surface, and the raceway surface of the inner ring 22 on its lower surface. It is formed in a trapezoidal cross section having an inclined surface 23b that can come into surface contact with 22a. A concave portion 23a1 for storing lubricating oil is formed over the entire circumference at an intermediate portion of the inclined surface 23a of the sliding body 23, and a concave portion for storing lubricating oil is formed at an intermediate portion of the inclined surface 23b of the sliding body 23. 23b1 is formed over the entire circumference.

外輪２１と内輪２２は、摺動体２３を介在させた状態で、外輪２１の係合部２１ｃと内輪２２の係合部２２ｃとが係り合い、外輪２１の係合部２１ｄと内輪２２の係合部２２ｄとが係り合うことで一体的に結合され、結合後の分離が規制されるようになっている。また、この結合状態では、係合部２１ｃ，２２ｃ間にラビリンス状の極僅かな隙間Ｔ１が形成され、係合部２１ｄ，２２ｄ間にラビリンス状の極僅かな隙間Ｔ２が形成されている。なお、外輪２１の内側部と内輪２２の内側部間には、所定量の潤滑油が封入されている。   The outer ring 21 and the inner ring 22 are engaged with the engaging part 21c of the outer ring 21 and the engaging part 22c of the inner ring 22 with the sliding body 23 interposed therebetween, and the engaging part 21d of the outer ring 21 and the inner ring 22 are engaged. By being engaged with the portion 22d, they are integrally coupled, and separation after the coupling is regulated. In this coupled state, a labyrinth-like very small gap T1 is formed between the engaging portions 21c and 22c, and a labyrinth-like very little gap T2 is formed between the engaging portions 21d and 22d. A predetermined amount of lubricating oil is sealed between the inner part of the outer ring 21 and the inner part of the inner ring 22.

上記のように構成した第１実施形態においては、摺動体２３の厚みが径方向外方に向かうに従って増加するように、すなわち、外輪２１の軌道面２１ａとの接触面である摺動体２３の傾斜面２３ａが、ストラット軸線Ｌ１と車両上方側にて交差する法線Ｌ２を有するように傾斜面２３ａの傾斜方向が設定されている。また、内輪２２の軌道面２２ａとの接触面である摺動体２３の傾斜面２３ｂが、ストラット軸線Ｌ１と車両下方側にて交差する法線Ｌ３を有するように傾斜面２３ｂの傾斜方向が設定されている。   In the first embodiment configured as described above, the thickness of the sliding body 23 increases as it goes radially outward, that is, the inclination of the sliding body 23 that is a contact surface with the raceway surface 21 a of the outer ring 21. The inclination direction of the inclined surface 23a is set so that the surface 23a has a normal line L2 that intersects the strut axis L1 on the vehicle upper side. Further, the inclination direction of the inclined surface 23b is set so that the inclined surface 23b of the sliding body 23 that is a contact surface with the raceway surface 22a of the inner ring 22 has a normal line L3 that intersects the strut axis L1 on the vehicle lower side. ing.

これにより、コイルスプリング１２からアッパースプリングシート１４を経て内輪２２に横荷重が作用した場合には、楔の原理により摺動体２３から外輪２１に対してストラット軸方向の荷重が付与される。そして、この荷重は外輪２１からアッパーサポート１３を経て車体ＢＤに付与されるので、結果として横荷重が負荷されることになる。   As a result, when a lateral load acts on the inner ring 22 from the coil spring 12 through the upper spring seat 14, a load in the strut axial direction is applied from the sliding body 23 to the outer ring 21 by the wedge principle. Since this load is applied from the outer ring 21 to the vehicle body BD via the upper support 13, a lateral load is applied as a result.

また、上記第１実施形態においては、外輪２１、内輪２２および摺動体２３が樹脂で形成され、摺動体２３の両傾斜面２３ａ，２３ｂには、油溜め用の凹部２３ａ１，２３ｂ１が形成されている。これにより、凹部２３ａ１，２３ｂ１内に潤滑油が溜められるので、アッパースプリングシート１４のアッパーサポート１３に対するストラット軸線Ｌ１回りの回転時において、内外輪２１，２２と摺動体２３間の摩擦抵抗を効果的に低減することが可能である。   In the first embodiment, the outer ring 21, the inner ring 22 and the sliding body 23 are made of resin, and the oil reservoirs 23a1 and 23b1 are formed on both inclined surfaces 23a and 23b of the sliding body 23. Yes. As a result, since the lubricating oil is stored in the recesses 23a1 and 23b1, the frictional resistance between the inner and outer rings 21 and 22 and the sliding body 23 is effectively improved when the upper spring seat 14 rotates around the strut axis L1 with respect to the upper support 13. It is possible to reduce it.

また、上記第１実施形態において、外輪２１と内輪２２には、摺動体２３を介在させた状態で外輪２１と内輪２２とを一体的に結合する係合部２１ｃ，２１ｄ、２２ｃ，２２ｄが形成されている。これにより、外輪２１、内輪２２および摺動体２３の組み付けが容易となり、組み付け後に分離（ばらけ）し難い構造とすることが可能である。また、隙間Ｔ１，Ｔ２によるラビリンス効果により防塵効果が良好となり、内部に封入された潤滑油の外部への漏れを効果的に防止することも可能である。   In the first embodiment, the outer ring 21 and the inner ring 22 are formed with engaging portions 21c, 21d, 22c, and 22d that integrally couple the outer ring 21 and the inner ring 22 with the sliding body 23 interposed therebetween. Has been. As a result, the outer ring 21, the inner ring 22 and the sliding body 23 can be easily assembled, and a structure that is difficult to separate (separate) after the assembly can be obtained. Further, the labyrinth effect by the gaps T1 and T2 provides a good dustproof effect, and it is also possible to effectively prevent leakage of the lubricating oil sealed inside.

（第２実施形態）
上記第１実施形態に係る軸受２０においては、摺動体２３における内輪２２の軌道面２２ａとの接触面を、ストラット軸線Ｌ１と車両下方側にて交差する法線Ｌ３を有する傾斜面２３ｂとしたが、これに代えて、例えば図４に示すように、摺動体２３における内輪２２の軌道面２２ａとの接触面を、ストラット軸線Ｌ１と直交する水平面２３ｂとしてもよい。これに対応して、内輪２２の軌道面２２ａも水平状に形成される。 (Second Embodiment)
In the bearing 20 according to the first embodiment, the contact surface of the sliding body 23 with the raceway surface 22a of the inner ring 22 is the inclined surface 23b having the normal line L3 that intersects the strut axis L1 on the vehicle lower side. Instead of this, for example, as shown in FIG. 4, the contact surface of the sliding body 23 with the raceway surface 22a of the inner ring 22 may be a horizontal surface 23b orthogonal to the strut axis L1. Correspondingly, the raceway surface 22a of the inner ring 22 is also formed horizontally.

この第２実施形態に係る軸受１２０においても、上記第１実施形態と同様、横荷重が負荷されるようになる。なお、この第２実施形態の他の構成については、上記第１実施形態と同様であるので、上記第１実施形態と同じ部材または同じ機能を果たす部位には同一の符号を付して、詳細な説明は省略する。   Also in the bearing 120 according to the second embodiment, a lateral load is applied as in the first embodiment. Since other configurations of the second embodiment are the same as those of the first embodiment, the same reference numerals are given to the same members or parts that perform the same functions as those of the first embodiment, and the details will be described. The detailed explanation is omitted.

（第３実施形態）
上記第１および第２実施形態においては、摺動体２３の厚みが径方向外方に向かうに従って増加するように、傾斜面２３ａ，２３ｂの傾斜方向を設定したが、これに代えて、例えば図５に示すように、摺動体２３の厚みが径方向内方に向かうに従って増加するように、すなわち、外輪２１の軌道面２１ａとの接触面である摺動体２３の傾斜面２３ａが、ストラット軸線Ｌ１と車両下方側にて交差する法線Ｌ２を有するように傾斜面２３ａの傾斜方向を設定し、内輪２２の軌道面２２ａとの接触面である摺動体２３の傾斜面２３ｂが、ストラット軸線Ｌ１と車両上方側にて交差する法線Ｌ３を有するように傾斜面２３ｂの傾斜方向を設定してもよい。 (Third embodiment)
In the first and second embodiments, the inclination directions of the inclined surfaces 23a and 23b are set so that the thickness of the sliding body 23 increases as it goes radially outward. Instead, for example, FIG. As shown in FIG. 3, the inclined surface 23a of the sliding body 23, which is a contact surface with the raceway surface 21a of the outer ring 21, is increased with the strut axis L1 so that the thickness of the sliding body 23 increases inward in the radial direction. The inclination direction of the inclined surface 23a is set so as to have a normal line L2 intersecting on the vehicle lower side, and the inclined surface 23b of the sliding body 23 which is a contact surface with the raceway surface 22a of the inner ring 22 is connected to the strut axis L1 and the vehicle. The inclination direction of the inclined surface 23b may be set so as to have a normal line L3 that intersects on the upper side.

この第３実施形態に係る軸受２２０においても、上記第１実施形態と同様、横荷重が負荷されるようになる。なお、この第３実施形態の他の構成については、上記第１実施形態と同様であるので、上記第１実施形態と同じ部材または同じ機能を果たす部位には同一の符号を付して、詳細な説明は省略する。   Also in the bearing 220 according to the third embodiment, a lateral load is applied as in the first embodiment. Since the other configurations of the third embodiment are the same as those of the first embodiment, the same members or the same functions as those of the first embodiment are denoted by the same reference numerals, and the details are as follows. The detailed explanation is omitted.

（第４実施形態）
上記第１〜第３実施形態においては、摺動体２３の傾斜面２３ａ，２３ｂの中間部位に、潤滑油を溜めるための凹部２３ａ１，２３ｂ１を形成したが、これに代えて、例えば図６に示すように、摺動体２３の傾斜面２３ａに対応する外輪２１の軌道面２１ａに凹部２１ａ１を全周に渡って形成し、摺動体２３の傾斜面２３ｂに対応する内輪２２の軌道面２２ａに凹部２２ａ１を全周に渡って形成してもよい。 (Fourth embodiment)
In the first to third embodiments, the recesses 23a1 and 23b1 for storing the lubricating oil are formed at the intermediate portions of the inclined surfaces 23a and 23b of the sliding body 23. Instead, for example, as shown in FIG. As described above, the recess 21a1 is formed over the entire circumference on the raceway surface 21a of the outer ring 21 corresponding to the inclined surface 23a of the slide body 23, and the recess 22a1 is formed on the track surface 22a of the inner ring 22 corresponding to the inclined surface 23b of the slide body 23. May be formed over the entire circumference.

この第４実施形態に係る軸受３２０においても、上記各実施形態と同様、内外輪２１，２２と摺動体２３間の摩擦抵抗を効果的に低減することが可能である。なお、この第４実施形態の他の構成については、上記第１実施形態と同様であるので、上記第１実施形態と同じ部材または同じ機能を果たす部位には同一の符号を付して、詳細な説明は省略する。   Also in the bearing 320 according to the fourth embodiment, it is possible to effectively reduce the frictional resistance between the inner and outer rings 21 and 22 and the sliding body 23 as in the above embodiments. In addition, since it is the same as that of the said 1st Embodiment about the other structure of this 4th Embodiment, the same code | symbol is attached | subjected to the part which performs the same member or the same function as the said 1st Embodiment, and details The detailed explanation is omitted.

上記第１〜第３実施形態においては、摺動体２３の傾斜面２３ａ，２３ｂの全周に渡って潤滑油を溜めるための凹部２３ａ１，２３ｂ１を形成したが、周方向の一領域のみに形成してもよいし、周方向の複数の領域に形成してもよい。また、第４実施形態においては、内外輪２１，２２の軌道輪２１ａ，２２ａの全周に渡って潤滑油を溜めるための凹部２１ａ１，２２ａ１を形成したが、周方向の一領域のみに形成してもよいし、周方向の複数の領域に形成してもよい。また、周方向に限らず、例えば図７にて摺動体２３を代表して示すように、摺動体２３の傾斜面２３ａ，２３ｂまたは内外輪２１，２２の軌道輪２１ａ，２２ａの径方向に形成してもよい。   In the first to third embodiments, the recesses 23a1 and 23b1 for storing the lubricating oil are formed over the entire circumference of the inclined surfaces 23a and 23b of the sliding body 23. However, the recesses 23a1 and 23b1 are formed only in one region in the circumferential direction. It may be formed in a plurality of regions in the circumferential direction. Further, in the fourth embodiment, the recesses 21a1 and 22a1 for storing the lubricating oil are formed over the entire circumference of the raceways 21a and 22a of the inner and outer rings 21 and 22. However, the recesses 21a1 and 22a1 are formed only in one region in the circumferential direction. It may be formed in a plurality of regions in the circumferential direction. Further, not limited to the circumferential direction, for example, as shown representatively of the sliding body 23 in FIG. 7, it is formed in the radial direction of the inclined surfaces 23 a and 23 b of the sliding body 23 or the raceways 21 a and 22 a of the inner and outer rings 21 and 22. May be.

本発明の第１実施形態に係るストラット軸受を採用したストラット上部の縦断面図。The longitudinal cross-sectional view of the upper part of the strut which employ | adopted the strut bearing which concerns on 1st Embodiment of this invention. 図１に示したストラット軸受の要部拡大図。The principal part enlarged view of the strut bearing shown in FIG. 図１の３−３矢視図。FIG. 3 is a view taken along arrow 3-3 in FIG. 1. 本発明の第２実施形態に係るストラット軸受の要部拡大図。The principal part enlarged view of the strut bearing which concerns on 2nd Embodiment of this invention. 本発明の第３実施形態に係るストラット軸受の要部拡大図。The principal part enlarged view of the strut bearing which concerns on 3rd Embodiment of this invention. 本発明の第４実施形態に係るストラット軸受の要部拡大図。The principal part enlarged view of the strut bearing which concerns on 4th Embodiment of this invention. 本発明の変形実施形態に係る摺動体の平面図。The top view of the sliding body which concerns on the deformation | transformation embodiment of this invention.

符号の説明Explanation of symbols

ＢＤ 車体
Ｌ１ ストラット軸線
１１ ショックアブソーバ
１２ コイルスプリング
１３ アッパーサポート
１４ アッパースプリングシート
２０，１２０，２２０，３２０ ストラット軸受
２１ 外輪
２１ａ 軌道面
Ｌ２ 法線
２１ｂ 段部
２１ｃ，２１ｄ 係合部
２２ 内輪
２２ａ 軌道面
Ｌ３ 法線
２２ｂ 段部
２２ｃ，２２ｄ 係合部
２３ 摺動体
２３ａ，２３ｂ 傾斜面
２３ａ１，２３ｂ１ 凹部
Ｔ１，Ｔ２ 隙間 BD Car body L1 Strut axis 11 Shock absorber 12 Coil spring 13 Upper support 14 Upper spring seat 20, 120, 220, 320 Strut bearing 21 Outer ring 21a Track surface L2 Normal line 21b Stepped portion 21c, 21d Engaging portion 22 Inner ring 22a Track surface L3 Normal line 22b Stepped portion 22c, 22d Engaging portion 23 Sliding body 23a, 23b Inclined surface 23a1, 23b1 Recess T1, T2 Clearance

Claims (3)

車体に取り付けられるアッパーサポートと、ストラットに取り付けられるアッパースプリングシート間に介装され、前記アッパースプリングシートの前記アッパーサポートに対するストラット軸線回りの回転を許容するストラット軸受において、
前記アッパーサポートに固定された外輪と、
前記アッパースプリングシートに固定された内輪とを備え、
前記外輪と前記内輪間には、前記外輪の軌道面との接触面および前記内輪の軌道面との接触面のうちの少なくとも一方の接触面の法線が前記ストラット軸線と交差する傾斜面に形成された環状の摺動体が配置されていることを特徴とするストラット軸受。 In a strut bearing interposed between an upper support attached to a vehicle body and an upper spring seat attached to a strut and allowing rotation of the upper spring seat around the strut axis with respect to the upper support.
An outer ring fixed to the upper support;
An inner ring fixed to the upper spring seat,
Between the outer ring and the inner ring, a normal line of at least one of a contact surface with the raceway surface of the outer ring and a contact surface with the raceway surface of the inner ring is formed on an inclined surface intersecting the strut axis. A strut bearing characterized in that an annular sliding body is arranged. 前記外輪、前記内輪および前記摺動体は樹脂で形成され、前記外輪と前記内輪との両軌道面または前記摺動体の両接触面には、油溜め用の凹部が形成されている請求項１に記載のストラット軸受。   The outer ring, the inner ring, and the sliding body are made of resin, and recesses for oil sumps are formed on both raceway surfaces of the outer ring and the inner ring or on both contact surfaces of the sliding body. The described strut bearing. 前記外輪および前記内輪は、前記摺動体を介在させた状態で互いに係合して前記外輪と前記内輪とを一体的に結合する係合部を備えてなる請求項１または２に記載のストラット軸受。   3. The strut bearing according to claim 1, wherein the outer ring and the inner ring are provided with an engaging portion that engages with each other with the sliding body interposed therebetween and integrally couples the outer ring and the inner ring. 4. .
JP2007011389A 2007-01-22 2007-01-22 Strut bearing Pending JP2008175349A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2007011389A JP2008175349A (en) 2007-01-22 2007-01-22 Strut bearing

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2007011389A JP2008175349A (en) 2007-01-22 2007-01-22 Strut bearing

Publications (1)

Publication Number Publication Date
JP2008175349A true JP2008175349A (en) 2008-07-31

Family

ID=39702509

Family Applications (1)

Application Number Title Priority Date Filing Date
JP2007011389A Pending JP2008175349A (en) 2007-01-22 2007-01-22 Strut bearing

Country Status (1)

Country Link
JP (1) JP2008175349A (en)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2013065273A1 (en) * 2011-11-02 2013-05-10 オイレス工業株式会社 Synthetic resin slide bearing
JP2015190555A (en) * 2014-03-28 2015-11-02 カヤバ工業株式会社 Shock absorber
WO2015170586A1 (en) * 2014-05-09 2015-11-12 オイレス工業株式会社 Thrust sliding bearing
EP3290726A4 (en) * 2015-04-28 2018-11-07 Oiles Corporation Sliding bearing
EP3534024A4 (en) * 2016-10-27 2020-07-08 Oiles Corporation Sliding bearing
EP3693625A4 (en) * 2017-10-06 2021-07-07 Oiles Corporation Slide bearing

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS58175237A (en) * 1982-04-06 1983-10-14 Toshiba Corp Color picture tube
JPS6340621A (en) * 1986-08-05 1988-02-22 Honda Motor Co Ltd Casting die for trimming and is production
JPH02141722A (en) * 1988-09-28 1990-05-31 Ioptex Res Inc Contact lens and material thereof
JPH08159160A (en) * 1994-12-01 1996-06-18 Oiles Ind Co Ltd Synthetic resin thrust bearing
JP2002089568A (en) * 2000-09-18 2002-03-27 Ntn Corp Thrust rolling bearing
JP2003269458A (en) * 2002-03-14 2003-09-25 Oiles Ind Co Ltd Synthetic resinous thrust slide bearing
JP2006200672A (en) * 2005-01-21 2006-08-03 Jtekt Corp Thrust roller bearing

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS58175237A (en) * 1982-04-06 1983-10-14 Toshiba Corp Color picture tube
JPS6340621A (en) * 1986-08-05 1988-02-22 Honda Motor Co Ltd Casting die for trimming and is production
JPH02141722A (en) * 1988-09-28 1990-05-31 Ioptex Res Inc Contact lens and material thereof
JPH08159160A (en) * 1994-12-01 1996-06-18 Oiles Ind Co Ltd Synthetic resin thrust bearing
JP2002089568A (en) * 2000-09-18 2002-03-27 Ntn Corp Thrust rolling bearing
JP2003269458A (en) * 2002-03-14 2003-09-25 Oiles Ind Co Ltd Synthetic resinous thrust slide bearing
JP2006200672A (en) * 2005-01-21 2006-08-03 Jtekt Corp Thrust roller bearing

Cited By (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9400015B2 (en) 2011-11-02 2016-07-26 Oiles Corporation Synthetic resin-made sliding bearing
JP2013096534A (en) * 2011-11-02 2013-05-20 Oiles Corp Synthetic resin slide bearing
CN103906937A (en) * 2011-11-02 2014-07-02 奥依列斯工业株式会社 Synthetic resin slide bearing
US9039285B2 (en) 2011-11-02 2015-05-26 Oiles Corporation Synthetic resin-made sliding bearing
RU2562889C1 (en) * 2011-11-02 2015-09-10 Оилз Корпорейшн Journal bearing from synthetic resin
WO2013065273A1 (en) * 2011-11-02 2013-05-10 オイレス工業株式会社 Synthetic resin slide bearing
CN105697538A (en) * 2011-11-02 2016-06-22 奥依列斯工业株式会社 Synthetic resin-made sliding bearing
JP2015190555A (en) * 2014-03-28 2015-11-02 カヤバ工業株式会社 Shock absorber
WO2015170586A1 (en) * 2014-05-09 2015-11-12 オイレス工業株式会社 Thrust sliding bearing
US10060471B2 (en) 2014-05-09 2018-08-28 Oiles Corporation Thrust sliding bearing
EP3290726A4 (en) * 2015-04-28 2018-11-07 Oiles Corporation Sliding bearing
US10344799B2 (en) 2015-04-28 2019-07-09 Oiles Corporation Sliding bearing
EP3534024A4 (en) * 2016-10-27 2020-07-08 Oiles Corporation Sliding bearing
EP3693625A4 (en) * 2017-10-06 2021-07-07 Oiles Corporation Slide bearing
US11231068B2 (en) 2017-10-06 2022-01-25 Giles Corporation Slide bearing

Similar Documents

Publication Publication Date Title
JP4288930B2 (en) Plain bearing
KR101134667B1 (en) Thrust slide bearing
RU2583986C2 (en) Plain thrust bearing
JP5950623B2 (en) Thrust sliding bearing and combination mechanism of thrust sliding bearing and piston rod
JP2017207124A (en) Bearing device for wheel
US10415657B2 (en) One-way bearing
JP2000145800A (en) Strut bearing
JP5842402B2 (en) Thrust sliding bearing
JP2008175349A (en) Strut bearing
JP2012172814A (en) Thrust sliding bearing made of synthetic resin
JP2007016972A (en) Thrust bearing and suspension for vehicle
JP5909976B2 (en) Synthetic plastic plain bearing
JP2012229763A (en) Seal structure
JP2013231470A (en) Sealing structure
JP6260784B2 (en) Thrust sliding bearing and spring pad integrated elastic seal member used therefor
JP6710566B2 (en) Bearing device, assembly, and sealing device
JP2008232403A (en) Bearing unit for strut
JP4853660B2 (en) Strut bearing unit
CN108291576B (en) Synthetic resin sliding bearing
JP4380177B2 (en) Thrust sliding bearing
JP2006322505A (en) Thrust bearing
JP7046514B2 (en) Sealing device
JP5708403B2 (en) Sealing device for bearing
JP2012013228A (en) Motor vehicle bump stop comprising set of at least two mounted seal ring
JP2015224746A (en) Rolling bearing device for wheel

Legal Events

Date Code Title Description
A621 Written request for application examination

Free format text: JAPANESE INTERMEDIATE CODE: A621

Effective date: 20091215

A977 Report on retrieval

Free format text: JAPANESE INTERMEDIATE CODE: A971007

Effective date: 20110414

A131 Notification of reasons for refusal

Free format text: JAPANESE INTERMEDIATE CODE: A131

Effective date: 20110418

A521 Written amendment

Free format text: JAPANESE INTERMEDIATE CODE: A523

Effective date: 20110524

A02 Decision of refusal

Free format text: JAPANESE INTERMEDIATE CODE: A02

Effective date: 20120105