JPH03277809A - Oscillating bearing - Google Patents
Oscillating bearingInfo
- Publication number
- JPH03277809A JPH03277809A JP2075256A JP7525690A JPH03277809A JP H03277809 A JPH03277809 A JP H03277809A JP 2075256 A JP2075256 A JP 2075256A JP 7525690 A JP7525690 A JP 7525690A JP H03277809 A JPH03277809 A JP H03277809A
- Authority
- JP
- Japan
- Prior art keywords
- roller
- elastic
- steel
- retainer
- 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
Links
- 229910000831 Steel Inorganic materials 0.000 claims abstract description 20
- 239000010959 steel Substances 0.000 claims abstract description 20
- 239000013013 elastic material Substances 0.000 claims abstract description 6
- 239000012530 fluid Substances 0.000 claims abstract description 6
- 238000006073 displacement reaction Methods 0.000 abstract description 10
- 230000007246 mechanism Effects 0.000 abstract description 7
- 229920001875 Ebonite Polymers 0.000 abstract description 3
- 229920002545 silicone oil Polymers 0.000 abstract description 2
- 230000006866 deterioration Effects 0.000 abstract 2
- 230000000717 retained effect Effects 0.000 abstract 1
- 238000005096 rolling process Methods 0.000 description 11
- 230000010349 pulsation Effects 0.000 description 6
- 230000000694 effects Effects 0.000 description 5
- 238000005498 polishing Methods 0.000 description 3
- 230000002265 prevention Effects 0.000 description 3
- 230000003746 surface roughness Effects 0.000 description 3
- 239000002184 metal Substances 0.000 description 2
- 229910052751 metal Inorganic materials 0.000 description 2
- RYGMFSIKBFXOCR-UHFFFAOYSA-N Copper Chemical compound [Cu] RYGMFSIKBFXOCR-UHFFFAOYSA-N 0.000 description 1
- 238000010521 absorption reaction Methods 0.000 description 1
- 229910052802 copper Inorganic materials 0.000 description 1
- 239000010949 copper Substances 0.000 description 1
- 230000005489 elastic deformation Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000020169 heat generation Effects 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
- 238000005086 pumping Methods 0.000 description 1
- 230000003252 repetitive effect Effects 0.000 description 1
- 239000007787 solid Substances 0.000 description 1
- 230000003068 static effect Effects 0.000 description 1
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
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/50—Other types of ball or roller bearings
- F16C19/502—Other types of ball or roller bearings with rolling elements in rows not forming a full circle
-
- 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
- F16C27/00—Elastic or yielding bearings or bearing supports, for exclusively rotary movement
- F16C27/04—Ball or roller bearings, e.g. with resilient rolling bodies
-
- 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
- F16C33/30—Parts of ball or roller bearings
- F16C33/306—Means to synchronise movements
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Reciprocating Pumps (AREA)
- Details Of Reciprocating Pumps (AREA)
- Support Of The Bearing (AREA)
- Rolling Contact Bearings (AREA)
Abstract
Description
【発明の詳細な説明】
〔産業上の利用分野〕
本発明は、可変容量形プランジャポンプの可変容量機構
等に使用される揺動軸受に関するものである。DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a rocking bearing used in a variable displacement mechanism of a variable displacement plunger pump, etc.
第４図は揺動軸受が使用される装置の一例として、可変
容量型プランジャポンプを示す。この可変容量型プラン
ジャポンプは、駆動軸（１１）にシリンダバレル（１２
）を取り付け、シリンダバレル（１２）に設けた複数の
シリンダ（１３）内にプランジャ（１４）をスライド自
在に挿入し、駆動軸（１１）の軸方向に傾斜させた半円
柱状のスワツシュブレー）（１５）をシリンダバレル（
１２）に対向配置すると共に、駆動軸（１１）の回転に
よってプランジャ（１４）の先端をスワッシュプレート
（１５）のプランジャ揺動面（１６）に沿って摺動せし
め、プランジャ（１４）を軸方向に往復運動させること
によってポンプ作用を行う。FIG. 4 shows a variable displacement plunger pump as an example of a device using a swing bearing. This variable displacement plunger pump has a cylinder barrel (12) attached to a drive shaft (11).
), the plunger (14) is slidably inserted into a plurality of cylinders (13) provided in the cylinder barrel (12), and a semi-cylindrical swash brake () ( 15) Attach the cylinder barrel (
12), and the tip of the plunger (14) is slid along the plunger swinging surface (16) of the swash plate (15) by rotation of the drive shaft (11), so that the plunger (14) is moved in the axial direction. Pumping action is performed by making the pump reciprocate.
スワッシュプレート（１５）はハネ（１７）によって、
円弧状面（１８）とケーシング（１９）との間に配置さ
れた円弧状の揺動軸受（２０）に圧接されている。揺動
軸受（２０）は、第５図に示す様に、円弧状の保持器（
２１）と、保持器（２１）の周方向に等間隔に形成され
た複数のポケソ） （２３）に収納されたころ（２４）
と、保持器（２１）の外周側に装着される軌道輪（２２
）とから成り、スワラシャプレート（１５）の軸方向に
２個を一対として配置されている。吐出量の調節は、こ
の圧接されたスワッシュプレート（１５）を駆動軸（１
１）の軸方向に揺動させてプランジ＋（１４）のストロ
ークを変化させることによって行う。The swash plate (15) is attached by the blade (17).
It is pressed into contact with an arcuate swing bearing (20) disposed between the arcuate surface (18) and the casing (19). As shown in FIG. 5, the rocking bearing (20) has an arcuate retainer (
21) and a plurality of rollers (24) housed in a plurality of rollers (23) formed at equal intervals in the circumferential direction of the cage (21).
and a bearing ring (22) attached to the outer peripheral side of the retainer (21).
), which are arranged as a pair in the axial direction of the swarasher plate (15). To adjust the discharge amount, move this press-welded swash plate (15) to the drive shaft (1
1) by changing the stroke of the plunger (14) by swinging it in the axial direction.
スワッシュプレートは揺動する際、揺動軸受σ転動体の
回転によって案内されるが、スワッシュプレートに偏荷
重がかかった場合、転動体が周フ向に滑り、転動体を収
納する保持器が周方向にスレ動くおそれがある。従来、
このズレを防止すまためケーシングにズレ止め機構を設
けていたが、揺動軸受は、通常、軸方向に２個を一対と
して包用され、しかも、相互に非連結であるため、ズレ
止め機構はそれぞれの揺動軸受に対し設けなけねばなら
ない、その結果、ケーシングは二つのズレ止め機構を収
納し得るものでなければならず、馨ｆ部体が大型化する
という不都合があった。When the swashplate swings, it is guided by the rotation of the swash bearing σ rolling elements, but if an unbalanced load is applied to the swashplate, the rolling elements slide in the circumferential direction, causing the cage that houses the rolling elements to slide around the periphery. There is a risk of the thread moving in the direction. Conventionally,
In order to prevent this misalignment, the casing has been provided with an anti-slip mechanism, but swing bearings are usually packaged in pairs in the axial direction, and are not connected to each other, so the anti-slip mechanism cannot be used. As a result, the casing must be capable of accommodating two anti-slip mechanisms, resulting in an inconvenience that the f-section body becomes larger.
また、揺動軸受はスワッシュプレートを介してプランジ
中の往復運動によって発生する振動、油圧の脈動を受け
る。この振動、脈動によって転動体と転走面とが軸方向
に相対的なくり返し微小滑りを生じ、接触面が摩耗（フ
レッティング）する、その結果、軸受寿命が低下する。In addition, the swing bearing receives vibrations and hydraulic pulsations generated by the reciprocating motion during plunging via the swash plate. This vibration and pulsation cause the rolling elements and the raceway surfaces to repeatedly and repeatedly slide relative to each other in the axial direction, causing wear (fretting) of the contact surfaces, resulting in a shortened bearing life.
また、振動、脈動は、装置自体の耐久性にも悪影響を及
ぼす。Furthermore, vibrations and pulsations have a negative effect on the durability of the device itself.
また、転動体と転走面とがメタルタッチのため、接触面
には表面あらさに起因する高面圧が発生し、ころがり摩
擦抵抗の増大要因となる。この高面圧の発生を回避する
ため、転走面には通常、高精度の研磨仕上げをしている
。しかし、高精度の研磨仕上げは加工コスト、加工時間
の増大をもたらす。Furthermore, since the rolling elements and the raceway surface touch each other with metal, high surface pressure is generated on the contact surface due to surface roughness, which is a factor in increasing rolling friction resistance. In order to avoid the occurrence of this high surface pressure, the raceway surfaces are usually polished to a high precision. However, high-precision polishing results in increased processing costs and processing time.
本発明は、前記問題点に鑑みて提案されたもので、その
第一の目的はズレ止め機構を設けることなく保持器のズ
レを防止し得る揺動軸受を提供することにある。The present invention has been proposed in view of the above-mentioned problems, and its first purpose is to provide a rocking bearing that can prevent the cage from shifting without providing a slippage prevention mechanism.
本発明の第二の目的は、振動、脈動による軸受寿命の低
下、装置全体の耐久性の低下を防止することにある。A second object of the present invention is to prevent reduction in bearing life and durability of the entire device due to vibration and pulsation.
本発明の第三の目的は、転走面を高精度に研磨仕上げす
ることなく高面圧の発生を回避することにある。A third object of the present invention is to avoid the generation of high surface pressure without polishing the raceway surface with high precision.
本発明では保持器に複数のポケットを形成し、ポケット
に鋼製のころと、内部に流体を封入した弾性材料で形成
した弾性ころとを収納し、弾性ころの直径をころの直径
より僅かに大径とすることによって、軸受に負荷された
荷重が弾性ころによって支持されるようにした。In the present invention, a plurality of pockets are formed in the cage, and a steel roller and an elastic roller made of an elastic material with a fluid sealed inside are housed in the pocket, and the diameter of the elastic roller is made slightly smaller than the diameter of the roller. By making the bearing large in diameter, the load applied to the bearing is supported by the elastic rollers.
弾性ころは負荷された荷重によって弾性変形し、この弾
性変形によって振動、脈動を吸収する。The elastic rollers are elastically deformed by the applied load, and this elastic deformation absorbs vibrations and pulsations.
また、この変形は弾性ころと転走面との接触面積を増大
させ、接触面圧を実質的に低下させると共に、弾性ころ
と転走面との密着性を高め相互間の滑りを防止する。そ
の結果、保持器のズレおよび接触面のフレッティングが
防止される。また、表面あらさに起因する高面圧は、上
記接触面圧の低下に加え、転走面の表面の微小凸部が弾
性ころの微小変形によって吸収されるため、メタルタッ
チの場合に比べて著しく減少する。Further, this deformation increases the contact area between the elastic rollers and the raceway surface, substantially lowering the contact surface pressure, and increases the adhesion between the elastic rollers and the raceway surface to prevent slippage between them. As a result, displacement of the cage and fretting of the contact surface are prevented. In addition, the high contact pressure caused by the surface roughness is significantly more significant than in the case of metal touch, because in addition to the reduction in the contact pressure mentioned above, the small convexities on the surface of the raceway are absorbed by the small deformations of the elastic rollers. Decrease.
従来の鋼製のころは剛性が高く変形しないため、荷重が
負荷された場合、転走面に研磨仕上げを施した状態でも
、その接触面には略２００〜３００ ｋｇ／ｄの高面圧
が発生し、二〇面圧はころが転勤する際に転がり摩擦抵
抗となって転勤を妨げる。しかし、本発明の弾性ころは
、この高面圧を発生させず、しかも変形することによっ
て断面をキャタピラ状にして転勤するため、接触面には
せん断抵抗が生じるだけで転がり抵抗は殆ど生じない。Conventional steel rollers have high rigidity and do not deform, so when a load is applied, a high surface pressure of approximately 200 to 300 kg/d is applied to the contact surface even if the raceway surface is polished. The surface pressure generated becomes rolling friction resistance when the rollers are transferred, and prevents transfer. However, the elastic roller of the present invention does not generate this high surface pressure, and moreover, it deforms and rolls with a caterpillar-shaped cross section, so only shear resistance is generated on the contact surface, and almost no rolling resistance is generated.
従って、弾性ころの転勤は転走面の表面状態に影響され
ず、滑らかに転勤することができる。Therefore, the elastic rollers can be smoothly transferred without being affected by the surface condition of the rolling surface.
一方、弾性ころの内部に封入さた液体は弾性ころの変形
によって内圧が上昇し、この内圧によって、負荷された
荷重を支持する。従って、弾性ころを形成する弾性材料
自体には圧縮応力が殆ど生じない。そして、負荷された
荷重が大きく、弾性ころと鋼製ころの直径寸法差以上に
弾性ころが変形しようとした場合には、その荷重は剛性
の高い鋼製ころによって支持されるため、負荷側が軸受
方向に位置ズレしない。On the other hand, the internal pressure of the liquid sealed inside the elastic roller increases due to the deformation of the elastic roller, and this internal pressure supports the applied load. Therefore, almost no compressive stress is generated in the elastic material itself forming the elastic roller. If the applied load is large and the elastic roller attempts to deform by more than the difference in diameter between the elastic roller and the steel roller, the load will be supported by the highly rigid steel roller, so the load side will be supported by the bearing. The position will not shift in the direction.
無論、弾性ころの変形のくり返しおよび転勤によって、
弾性ころ内部の発熱、あるいは接触部の摩耗等が生じる
ことが考えられるが、前述したような種類の装置におい
ては、衝撃荷重、くり返し荷重に比べて静荷重、振動等
が多く作用し、また転動体の回転はあまり高くないのが
普通であるから特に問題はない。Of course, due to repeated deformation and transfer of the elastic rollers,
Heat generation inside the elastic rollers or wear of the contact parts may occur, but in the types of equipment mentioned above, static loads and vibrations act more frequently than impact loads and repetitive loads, and rolling Since the rotation of a moving object is usually not very high, there is no particular problem.
本発明の実施例を図面に基づいて説明する。 Embodiments of the present invention will be described based on the drawings.
第１図に示す様に、本発明に係る揺動軸受は円弧状の保
持器（１）と、保持器（１）の周方向に等間隔に形成さ
れた複数のポケット（３）に収納されたこる（４）と、
保持器（１）の外周側に装着される円弧状の軌道輪（２
）とから成っている。ころ（４）は、鋼製ころ（４ａ）
と、弾性材料、例えば硬質ゴム等で形成された弾性ころ
（４ｂ）とから成り、弾性ころ（４ｂ） （４ｂ）間
に二つの鋼製ころ（４ａ） （４ａ）が収納されるよ
うに配置している。また、第２図に示す様に、弾性ころ
（４ｂ）の中心部には非圧縮性の流体（５）、例えばシ
リコン油等が封入されている。また、弾性ころ（４ｂ）
は銅製ころ（４ａ）より若干、大径に形成し、通常の荷
重が負荷された状態では、弾性変形した弾性ころ（４ｂ
）によって全荷重が支えられるようにしている。そして
、最大荷重が生じた時に、同図に示すように、弾性ころ
（４ｂ）はδだけ変形し、この時初めて鋼製ころ（４ａ
）が軌道輪（２）の転走面（７）および負荷側（６）に
当接し荷重を支持するようにしている。従って、負荷側
（６）は軸受方向に最大でもδだけの位置ズレしかせず
、しかも硬質ゴムの場合δは微小であるから、負荷側（
６）は正確に位置決めされる。ポケット（３ｂ）はこの
変形量δを見込んで、鋼製ころ（４ａ）用のポケット（
３ａ）より若干、大きくしである。As shown in FIG. 1, the rocking bearing according to the present invention is housed in an arcuate retainer (1) and a plurality of pockets (3) formed at equal intervals in the circumferential direction of the retainer (1). Takoru (4) and
An arc-shaped bearing ring (2) is attached to the outer circumferential side of the retainer (1).
). The roller (4) is a steel roller (4a)
and an elastic roller (4b) made of an elastic material such as hard rubber, and arranged so that two steel rollers (4a) (4a) are housed between the elastic rollers (4b) (4b). are doing. Further, as shown in FIG. 2, an incompressible fluid (5), such as silicone oil, is sealed in the center of the elastic roller (4b). In addition, elastic rollers (4b)
is formed to have a slightly larger diameter than the copper roller (4a), and when a normal load is applied, the elastic roller (4b) is elastically deformed.
) so that the entire load can be supported. Then, when the maximum load occurs, the elastic roller (4b) deforms by δ, as shown in the figure, and only at this time does the steel roller (4a
) is in contact with the raceway surface (7) and load side (6) of the bearing ring (2) to support the load. Therefore, the load side (6) can only shift by δ at most in the bearing direction, and since δ is minute in the case of hard rubber, the load side (6)
6) is accurately positioned. Considering this deformation amount δ, the pocket (3b) is designed to accommodate the steel roller (4a) (
It is slightly larger than 3a).
第３図は本発明の第二の実施例を示し、保持器（１）に
鋼製ころ（４ａ）用のポケット（３ａ）と、弾性ころ（
４ｂ）を一対収納できるポケット（３Ｃ）を設けている
。これは、保持器全体に収納し得る弾性ころ（４ｂ）の
数を増やすためである。その結果、軸受負荷容量が増大
すると共に、保持器のズレ止め、振動吸収等の機能が向
上する。勿論、鋼製ころ（４ａ）も同じように一対収納
してもよい。FIG. 3 shows a second embodiment of the present invention, in which the cage (1) has pockets (3a) for steel rollers (4a) and elastic rollers (
There is a pocket (3C) that can store a pair of items 4b). This is to increase the number of elastic rollers (4b) that can be housed in the entire cage. As a result, the bearing load capacity is increased, and functions such as retainer displacement prevention and vibration absorption are improved. Of course, a pair of steel rollers (4a) may also be stored in the same manner.
この場合は軸受負荷容量が増大する。また、ポケットを
大きくして二辺上の数のころを同一ポケット内に収納し
てもよいし、鋼製ころ（４ａ）と弾性ころ（４ｂ）とを
同一ポケット内に収納するようにしてもよい。In this case, the bearing load capacity increases. Also, the pocket may be made larger and the number of rollers on two sides may be stored in the same pocket, or the steel rollers (4a) and elastic rollers (4b) may be stored in the same pocket. good.
尚、保持器（１）は第２図に示す様に、ポケットを円筒
状にした転動体案内方式または第３図に示す様に、ポケ
ットを通し穴にした軌道輪案内方式のいずれでもかまわ
ない。The cage (1) may be of either a rolling element guide type with cylindrical pockets as shown in Figure 2, or a bearing ring guide type with pockets as through holes as shown in Figure 3. .
また、前記二つの実施例では保持器および軌道輪を円弧
状のものとしたが、本発明はこれに限定されず、例えば
工作機械の案内面等に使用される直線軸受にも応用でき
、その場合、前記二つの実施例と同様の効果を有する。Further, in the above two embodiments, the retainer and bearing ring were arc-shaped, but the present invention is not limited to this, and can be applied to, for example, a linear bearing used as a guideway of a machine tool. In this case, it has the same effect as the above two embodiments.
尚、軸受に負荷される荷重が小さい場合には、むくの弾
性材料で形成した弾性ころを用いることも可能である。Incidentally, if the load applied to the bearing is small, it is also possible to use elastic rollers made of solid elastic material.
本発明によって以下の効果が得られる。 The present invention provides the following effects.
■ 弾性ころと転走面とは密着性が高いため、相互間の
滑りが生じない。そのため、揺動運動により保持器のズ
レがなくなり、ズレ止め機構が不要になる。その結果、
装置自体の小型軽量化が図れる。■ Elastic rollers and raceway surfaces have high adhesion, so no slippage occurs between them. Therefore, the holder does not shift due to the rocking motion, and a shift prevention mechanism becomes unnecessary. the result,
The device itself can be made smaller and lighter.
■ 軸受に作用する振動、脈動を弾性ころによって吸収
するため、フレッティングによる軸受寿命の低下、さら
には装置自体の耐久性低下を防止することができる。■ Vibration and pulsation acting on the bearing are absorbed by the elastic rollers, which prevents a reduction in bearing life due to fretting, as well as a reduction in the durability of the device itself.
■ 弾性ころと転走面との接触面には表面あらさに起因
する高面圧が発生しないため、転走面は特別精度良く仕
上げる必要がない。従って、高精度な研磨工程が不要に
なり、加工コスト、加工時間が減少し、加工性が著しく
向上する。■ Since high surface pressure due to surface roughness does not occur on the contact surface between the elastic roller and the raceway surface, the raceway surface does not need to be finished with particularly high precision. Therefore, a high-precision polishing step is no longer necessary, processing costs and processing time are reduced, and workability is significantly improved.
第１図は本発明に係る揺動軸受の斜視図、第２図は第１
図の断面図、
第３図は本発明の第二の実施例を示す断面図である。
第４図は可変容量形プランジャポンプの断面図、！喝唾
縫勅堝漣赦−伺燵回で・おう。
（１）−・保持器 （３） −ポケット（３ａ）
（３ｂ）
（４）
（４ａ）
（５）
鋼製ころ用のポケット
（３ｃ：ｌ−ｍ−弾性ころ用のポケットころ
−鋼製ころ （４ｂ）−弾性ころ
−流体FIG. 1 is a perspective view of a swing bearing according to the present invention, and FIG. 2 is a perspective view of a swing bearing according to the present invention.
FIG. 3 is a cross-sectional view showing a second embodiment of the present invention. Figure 4 is a cross-sectional view of a variable displacement plunger pump! Let's talk about this in the interview. (1) - Cage (3) - Pocket (3a) (3b) (4) (4a) (5) Pocket for steel roller (3c: l-m - Pocket roller for elastic roller - Steel roller (4b) - Elastic roller - Fluid
Claims (1)
のころと内部に流体を封入した弾性材料で形成した弾性
ころとを夫々収納し、かつ、該弾性ころの直径を前記こ
ろの直径より僅かに大径とした揺動軸受。(1) A plurality of pockets are provided in the cage, and each pocket accommodates a steel roller and an elastic roller made of an elastic material with a fluid sealed inside, and the diameter of the elastic roller is set to the diameter of the roller. Swing bearing with slightly larger diameter.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2075256A JPH03277809A (en) | 1990-03-24 | 1990-03-24 | Oscillating bearing |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2075256A JPH03277809A (en) | 1990-03-24 | 1990-03-24 | Oscillating bearing |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH03277809A true JPH03277809A (en) | 1991-12-09 |
Family
ID=13570957
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2075256A Pending JPH03277809A (en) | 1990-03-24 | 1990-03-24 | Oscillating bearing |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH03277809A (en) |
Cited By (14)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE10200609A1 (en) * | 2002-01-10 | 2003-07-24 | Ina Schaeffler Kg | Electrically assisted power steering for motor vehicles |
| DE10235285A1 (en) * | 2002-08-02 | 2004-02-12 | Ina-Schaeffler Kg | Belt drive motion dampening mechanism has rolling body in contact on both sides with inner face of outer body and outer face of inner body |
| GB2408078A (en) * | 2003-11-17 | 2005-05-18 | Timken Us Corp | A rolling contact bearing having both compressible and rigid rolling elements. |
| US6942417B2 (en) | 2000-05-19 | 2005-09-13 | Schwarzbich Joerg | Telescopic mechanism |
| DE102005048971A1 (en) * | 2005-10-13 | 2007-04-19 | Fag Kugelfischer Ag | Cylinder roller bearing for radial and axial suspension of shafts, has cylindrical roller bodies arranged between outer and inner rings and including respective eccentric borehole that extends parallel to longitudinal axis of roller bodies |
| DE102006019984A1 (en) * | 2006-04-29 | 2007-10-31 | Schaeffler Kg | Radial roller bearing, has drive disk that is formed at front surface and arranged at roller bodies to clamp bodies between running paths, where disk has larger diameter, and is deformable or adjustable in elastic region in radial direction |
| DE102006024376A1 (en) * | 2006-05-24 | 2007-11-29 | Schaeffler Kg | Rolling bearings with different guide pockets |
| DE102006044805A1 (en) * | 2006-09-22 | 2008-03-27 | Schaeffler Kg | Radial roller bearing, particularly for bearing partly small loaded shaft in heavy machines, has rolling elements, where individual rolling element is pressed independently on its extent position hydraulically over pressure oil pad |
| EP1921334A2 (en) * | 2006-11-09 | 2008-05-14 | Delphi Technologies, Inc. | Needle roller bearing |
| DE102006057451A1 (en) * | 2006-12-06 | 2008-06-12 | Schaeffler Kg | Bearing arrangement, especially for selector fork of transmission in motor vehicle, has at least one flexible body with enlarged rolling diameter to create vibration damping between shaft and outer bearing race |
| WO2008106933A1 (en) * | 2007-03-03 | 2008-09-12 | Schaeffler Kg | Radial anti-friction bearing, particularly cylinder roller bearing for the support of shafts in wind power gearboxes |
| DE102007013942A1 (en) | 2007-03-23 | 2008-09-25 | Schaeffler Kg | radial bearings |
| JP2013127277A (en) * | 2011-12-16 | 2013-06-27 | Ckd Corp | Guide member, linear guide and cylinder with guide |
| CN114981550A (en) * | 2020-02-12 | 2022-08-30 | 舍弗勒技术股份两合公司 | Segmented bearing arrangement with offset mounted rolling elements and pivot rod arrangement with said segmented bearing arrangement |
-
1990
- 1990-03-24 JP JP2075256A patent/JPH03277809A/en active Pending
Cited By (22)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6942417B2 (en) | 2000-05-19 | 2005-09-13 | Schwarzbich Joerg | Telescopic mechanism |
| DE10200609A1 (en) * | 2002-01-10 | 2003-07-24 | Ina Schaeffler Kg | Electrically assisted power steering for motor vehicles |
| US7032704B2 (en) | 2002-01-10 | 2006-04-25 | Ina-Schaeffler Kg | Electrically assisted, power steering system for motor vehicles |
| DE10235285A1 (en) * | 2002-08-02 | 2004-02-12 | Ina-Schaeffler Kg | Belt drive motion dampening mechanism has rolling body in contact on both sides with inner face of outer body and outer face of inner body |
| GB2408078A (en) * | 2003-11-17 | 2005-05-18 | Timken Us Corp | A rolling contact bearing having both compressible and rigid rolling elements. |
| DE102005048971A1 (en) * | 2005-10-13 | 2007-04-19 | Fag Kugelfischer Ag | Cylinder roller bearing for radial and axial suspension of shafts, has cylindrical roller bodies arranged between outer and inner rings and including respective eccentric borehole that extends parallel to longitudinal axis of roller bodies |
| DE102006019984A1 (en) * | 2006-04-29 | 2007-10-31 | Schaeffler Kg | Radial roller bearing, has drive disk that is formed at front surface and arranged at roller bodies to clamp bodies between running paths, where disk has larger diameter, and is deformable or adjustable in elastic region in radial direction |
| DE102006019984B4 (en) * | 2006-04-29 | 2017-10-26 | Schaeffler Technologies AG & Co. KG | radial bearings |
| DE102006024376A1 (en) * | 2006-05-24 | 2007-11-29 | Schaeffler Kg | Rolling bearings with different guide pockets |
| DE102006044805A1 (en) * | 2006-09-22 | 2008-03-27 | Schaeffler Kg | Radial roller bearing, particularly for bearing partly small loaded shaft in heavy machines, has rolling elements, where individual rolling element is pressed independently on its extent position hydraulically over pressure oil pad |
| DE102006044805B4 (en) * | 2006-09-22 | 2017-05-04 | Schaeffler Technologies AG & Co. KG | radial bearings |
| EP1921334A2 (en) * | 2006-11-09 | 2008-05-14 | Delphi Technologies, Inc. | Needle roller bearing |
| EP1921334A3 (en) * | 2006-11-09 | 2008-09-17 | Delphi Technologies, Inc. | Needle roller bearing |
| DE102006057451A1 (en) * | 2006-12-06 | 2008-06-12 | Schaeffler Kg | Bearing arrangement, especially for selector fork of transmission in motor vehicle, has at least one flexible body with enlarged rolling diameter to create vibration damping between shaft and outer bearing race |
| US8328429B2 (en) | 2007-03-03 | 2012-12-11 | Schaeffler Technologies AG & Co. KG | Radial anti-friction bearing, particularly cylinder roller bearing for the support of shafts in wind power gearboxes |
| KR101217018B1 (en) * | 2007-03-03 | 2013-01-02 | 섀플러 홀딩 게엠베하 운트 코. 카게 | Radial anti-friction bearing, particularly cylinder roller bearing for the support of shafts in wind power gearboxes |
| WO2008106933A1 (en) * | 2007-03-03 | 2008-09-12 | Schaeffler Kg | Radial anti-friction bearing, particularly cylinder roller bearing for the support of shafts in wind power gearboxes |
| DE102007013942A1 (en) | 2007-03-23 | 2008-09-25 | Schaeffler Kg | radial bearings |
| JP2013127277A (en) * | 2011-12-16 | 2013-06-27 | Ckd Corp | Guide member, linear guide and cylinder with guide |
| CN114981550A (en) * | 2020-02-12 | 2022-08-30 | 舍弗勒技术股份两合公司 | Segmented bearing arrangement with offset mounted rolling elements and pivot rod arrangement with said segmented bearing arrangement |
| US11982312B2 (en) | 2020-02-12 | 2024-05-14 | Schaeffler Technologies AG & Co. KG | Segment bearing device having offset mounting rolling element and pivot lever arrangement having said segment bearing device |
| CN114981550B (en) * | 2020-02-12 | 2024-09-20 | 舍弗勒技术股份两合公司 | Segmented bearing device with offset mounted rolling elements and pivot rod arrangement with the segmented bearing device |
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