WO2013031249A1 - スラスト軸受 - Google Patents
スラスト軸受 Download PDFInfo
- Publication number
- WO2013031249A1 WO2013031249A1 PCT/JP2012/051698 JP2012051698W WO2013031249A1 WO 2013031249 A1 WO2013031249 A1 WO 2013031249A1 JP 2012051698 W JP2012051698 W JP 2012051698W WO 2013031249 A1 WO2013031249 A1 WO 2013031249A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- thrust bearing
- cage
- glass fiber
- raceway surface
- raceway
- Prior art date
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Classifications
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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
- 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
- F16C33/38—Ball cages
- F16C33/3887—Details of individual pockets, e.g. shape or ball retaining means
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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
- 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
- F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
- F16C19/10—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for axial load mainly
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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
- 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
- F16C33/38—Ball cages
- F16C33/3837—Massive or moulded cages having cage pockets surrounding the balls, e.g. machined window cages
- F16C33/3843—Massive or moulded cages having cage pockets surrounding the balls, e.g. machined window cages formed as one-piece cages, i.e. monoblock cages
- F16C33/3856—Massive or moulded cages having cage pockets surrounding the balls, e.g. machined window cages formed as one-piece cages, i.e. monoblock cages made from plastic, e.g. injection moulded window cages
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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
- 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
- F16C33/38—Ball cages
- F16C33/44—Selection of substances
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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
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C2208/00—Plastics; Synthetic resins, e.g. rubbers
- F16C2208/02—Plastics; Synthetic resins, e.g. rubbers comprising fillers, fibres
- F16C2208/04—Glass fibres
-
- 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
- F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
- F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
- F16C2240/46—Gap sizes or clearances
Definitions
- the present invention relates to a thrust bearing used for a hydraulic continuously variable transmission, a hydraulic pump, a hydraulic motor, or the like.
- Thrust bearings are incorporated as bearings in hydraulic continuously variable transmissions, hydraulic pumps, hydraulic motors, and the like.
- a thrust bearing is employed in a portion that receives a piston pressure when converting the rotational force of the shaft into the hydraulic pressure or when converting the hydraulic pressure into the rotational force of the shaft (for example, Patent Document 1).
- Thrust bearings often use iron cages. However, when an eccentric load is applied, as in the case of thrust bearings for hydraulic continuously variable transmissions, impact is applied to the pocket surface due to the delay or advance of the ball, and the cage May be damaged.
- the present invention has been made in view of the above circumstances, and an object of the present invention is to provide a long-life thrust bearing that prevents breakage of the cage.
- the present invention provides the following thrust bearing.
- a first raceway having a first raceway surface, a second raceway having a second raceway surface, and freely rollable between the first raceway surface and the second raceway surface.
- the cage is made of synthetic resin, and the pocket gap is 2 to Thrust bearing characterized by 5%.
- the thrust bearing according to any one of (1) to (3) above, wherein the synthetic resin of the cage is polyamide.
- the thrust bearing according to any one of (1) to (4) above, wherein the synthetic resin of the cage has a number average molecular weight of 13000 to 30000.
- (6) The thrust bearing according to (5), wherein the cage is obtained by injection molding.
- the thrust bearing of the present invention is made of synthetic resin, preferably made of glass fiber-containing synthetic resin, and has a specific pocket clearance, so that it can effectively absorb the impact on the cage due to delay and advance of the ball, Long service life.
- FIG. 3 is a top view of FIG. 2. 6 is a graph showing the results of Test 2. 10 is a graph showing the results of Test 3.
- FIG. 1 is a cross-sectional view showing an example of a hydraulic continuously variable transmission.
- the hydraulic continuously variable transmission 30 is a variable capacity that converts a rotational driving force transmitted from an engine (not shown) to an input shaft 31 into an oil pressure.
- a pump 32 and a variable displacement motor 41 that returns the hydraulic pressure to the rotational driving force and transmits it to the output shaft 40 are provided, and the rotational driving force transmitted to the input shaft 31 is not used for the forward driving force and the backward driving force. It changes to a stage and outputs from the output shaft 40, or stops this output.
- the variable displacement pump 32 includes a cylinder block 33 that rotates integrally with the input shaft 31, a nose piston 35 that is reciprocated in the piston chamber 34, and a guide surface of the guide block 36. And a swash plate 37 rotating along the axis.
- the variable displacement pump 32 rotates the swash plate 37 to change the reciprocating stroke of the nose piston 35 and change the amount of oil discharged from the piston chamber 34.
- the thrust bearing 10 is disposed on the swash plate 37 at a position where the thrust bearing 10 contacts the tip of the nose piston 35, and the thrust bearing 10 rotates together with the swash plate 37.
- the thrust bearing 10 is fixed to the swash plate 37 and the first race ring 12 having the first raceway surface 11 in contact with the tip of the nose piston 35 at the end face 21 outside the bearing.
- the second raceway 14 having the second raceway surface 13 and a plurality of balls 15 arranged between the first raceway surface 11 and the second raceway surface 13 so as to roll freely.
- the thrust bearing 10 includes a cage 16 that holds a plurality of balls 15 at equal intervals in the circumferential direction.
- the cage 16 is made of synthetic resin.
- Polyamides such as aromatic polyamide, polyamide 46, and polyamide 66, are preferable when heat resistance, fatigue resistance, etc. are considered.
- Aromatic polyamide has a high melting point and high strength, and can be used at a high temperature of 130 to 150 ° C.
- Polyamide 46 also has a heat resistance of 120 to 140 ° C., and the resin itself has high impact strength and fatigue resistance.
- Polyamide 66 has a heat resistance of 100 to 120 ° C., but has a good balance of impact strength, fatigue resistance, etc., and a low material cost.
- the cage 16 preferably contains glass fibers for reinforcement.
- a glass fiber having a circular cross section can be used, but a cross section having an elliptical shape, an oval shape, an eyebrow shape, or the like is preferable.
- the glass fiber having an irregular cross section is less likely to be broken than the glass fiber having a circular cross section, and is dispersed in the resin in a longer state than the glass fiber having a circular cross section when kneaded with a resin and injection molded. Therefore, when compared with the same content, the reinforcing effect is higher than that of glass fibers having a circular cross section.
- the glass fiber having an irregular cross section is oriented so as to form a plane parallel to the cage surface during molding, it can receive a load on the surface, and has excellent load resistance, and also in the radial direction. A slight reinforcing effect appears and the reinforcing effect is further increased, and the difference in dimensional change is reduced, so that sink marks are less likely to occur.
- the deformed ratio (ratio of the major axis part to the minor axis part) of the glass fiber having an irregular cross section is preferably 1.5 to 5, and more preferably 2 to 4. If the profile ratio is less than 1.5, the effect of improving the mechanical strength is small, and if the profile ratio exceeds 5, it is too flat and it is difficult to produce stably.
- the minor axis portion is preferably 5 to 12 ⁇ m. If the short diameter part is less than 5 ⁇ m, it is too thin and breaks or breaks during production. Therefore, it is difficult to maintain a stable quality at low cost, and the practicality is low. On the other hand, when the minor axis exceeds 12 ⁇ m, the fiber is too thick in consideration of the deformed ratio, resulting in poor dispersibility in the resin, and unevenness in strength may occur in the resin part.
- a general synthetic resin cage has an average fiber diameter of about 10 to 13 ⁇ m, but preferably has an average fiber diameter of 6 to 8 ⁇ m.
- the above glass fiber is surface-treated with a silane coupling agent having an epoxy group or amino group at one end, or a sizing agent such as epoxy, urethane, or acrylic in consideration of adhesiveness with the resin. Is preferably used.
- the glass fiber content is preferably 20 to 40% by mass, more preferably 25 to 35% by mass of the total amount of the cage.
- the glass fiber content is less than 20% by mass, the reinforcing effect is not sufficient.
- the fluidity decreases and becomes unsuitable for injection molding.
- the retainer 16 is less likely to be bent, and the ball 15 is less likely to be incorporated during the assembly of the bearing.
- the upper limit of the glass fiber content is preferably 40% by mass, and more preferably 35% by mass.
- the number average molecular weight of the above resin is preferably from 13,000 to 30000, and further considering the mechanical strength such as impact strength, the number average molecular weight is more preferably from 18000 to 26000.
- the number average molecular weight is less than 13,000, the molecular weight is too low, the mechanical strength is low, and the practicality is low.
- the number average molecular weight exceeds 30000, the melt viscosity in a state where the glass fiber is contained in a specified amount is too high, and it becomes difficult to manufacture by injection molding with high accuracy.
- additives can be added to the above resin composition as necessary, but any of them may be added to a general synthetic resin cage.
- a part of glass fiber can be replaced with carbon fiber.
- the carbon fibers include pitch-based or PAN-based carbon fibers.
- it can be replaced by a whisker-like reinforcing material such as potassium titanate whisker or aluminum borate whisker.
- FIG.3 is a cross-sectional view showing a state in which the ball 15 is removed from FIG. 2
- FIG. 4 is a top view of FIG.
- the cage 16 has a plurality of pockets 17 formed in an annular base portion 16a, and further, a base portion 16a at a plurality of locations around the pocket 17 (four locations at equal intervals in the example in the figure).
- a claw portion 16b protruding outward is provided.
- the pocket-side surface 16c of the claw portion 16b is configured to be elastically deformed while standing substantially vertically so that the balls 15 can be easily inserted during assembly.
- the pocket clearance of the cage 16 is 2 to 5% of the diameter of the ball 15. That is, as shown in FIG. 4, the distance between the surface 15 a of the ball 15 and the pocket surface 17 a of the pocket 17 is 2 to 5% of the diameter of the ball 15.
- the pocket gap increases, the movement distance of the ball 15 increases and the impact on the pocket surface 17a also increases.
- the interval between the pockets is narrowed, and the column portion between the pockets is thinned, resulting in a decrease in strength. Therefore, the upper limit of the pocket gap with respect to the diameter of the ball 15 is 5%, and 4% is more preferable.
- the pocket clearance is less than 2% of the diameter of the ball 15, the maximum load on the retainer 16 is increased, resulting in a decrease in strength, which is not suitable.
- the thrust ball bearing of the present invention has been described as an example, but a roller or a tapered roller can be used as the rolling element.
- Test 1 Using an iron cage and a synthetic resin cage containing 25% by mass of glass fiber (sizing agent treated product, cross-section eyebrows) in polyamide 66, durability test under moment load conditions assuming ball delay and advance Went.
- a bearing “6204” manufactured by NSK Ltd. was used as a test bearing, and turbine oil was used as a lubricant.
- the pocket clearance of the synthetic resin cage was set to 3% of the ball diameter.
- the test conditions were a rotational speed of 2000 min ⁇ 1 , a moment load of 73.5 N ⁇ m, and an ambient temperature of 40 ° C. or 100 ° C. As a result, the iron cage was damaged within 20 hours, whereas the synthetic resin cage was not damaged even after 20 hours.
- Test 2 A test piece comprising a polyamide 66 alone, a resin composition containing 20% by mass of the glass fiber in polyamide 66, and a resin composition containing 30% by mass of the glass fiber in polyamide 66 is prepared, in accordance with ASTM D 671.
- a bending fatigue curve was created.
- the measurement atmosphere was a temperature of 23 ° C., a humidity of 85% RH, and the number of cycles was 1800 rpm.
- the results are shown in FIG.
- shaft S in a figure is a stress amplitude
- the horizontal axis N is the number of repetitions until a fracture
- the stress repeatedly increases as the glass fiber content increases.
- the stress amplitude is about 5 ⁇ 10 2 kgf / cm 2. Therefore, it can be seen that the glass fiber content should be 20% by mass or more.
- the thrust bearing of the present invention is useful for a hydraulic continuously variable transmission, a hydraulic pump, a hydraulic motor, and the like.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Rolling Contact Bearings (AREA)
- Injection Moulding Of Plastics Or The Like (AREA)
Abstract
Description
(1)第1の軌道面を有する第1の軌道輪と、第2の軌道面を有する第2の軌道輪と、前記第1の軌道面及び前記第2の軌道面間に転動自在に配置された複数の玉と、前記玉を円周方向に亘って等間隔に保持する保持器とを備えるスラスト軸受において、前記保持器が合成樹脂製で、かつ、ポケット隙間を玉径の2~5%としたことを特徴とするスラスト軸受。
(2)前記保持器が、ガラス繊維を20~40質量%の割合で含有することを特徴とする上記(1)記載のスラスト軸受。
(3)前記ガラス繊維が異形断面を有することを特徴とする上記(2)記載のスラスト軸受。
(4)前記保持器の合成樹脂がポリアミドであることを特徴とする上記(1)~(3)の何れか1項に記載のスラスト軸受。
(5)前記保持器の合成樹脂が数平均分子量で13000~30000であることを特徴とする上記(1)~(4)の何れか1項に記載のスラスト軸受。
(6)前記保持器が射出成形して得られることを特徴とする上記(5)記載のスラスト軸受。
鉄製保持器と、ポリアミド66にガラス繊維(サイジング剤処理品、断面まゆ形)を25質量%配合した合成樹脂製保持器とを用い、玉の遅れや進みを想定したモーメント荷重条件下で耐久試験を行った。試験軸受は日本精工株式会社製軸受「6204」を用い、潤滑剤としてタービン油を用いた。また、合成樹脂製保持器のポケット隙間を玉径の3%とした。試験条件は、回転数2000min-1、モーメント荷重73.5N・m、雰囲気温度40℃または100℃とした。その結果、鉄製保持器が20時間以内に破損したのに対し、合成樹脂製保持器は20時間を越えても破損しなかった。
ポリアミド66単独、ポリアミド66に同ガラス繊維を20質量%配合した樹脂組成物、ポリアミド66に同ガラス繊維を30質量%配合した樹脂組成物からなる試験片を用意し、ASTM D 671に準拠して曲げ疲労曲線を作成した。測定雰囲気は温度23℃、湿度85%RHとし、サイクル数を1800rpmとした。結果を図5に示す。尚、図中の縦軸Sは応力振幅であり、横軸Nは破断までの繰り返し数である。図示されるように、ガラス繊維の含有量が多くなるのに従って繰り返し応力が高まるが、一般的な油圧式無段変速機用スラスト軸受の保持器では応力振幅が5×102kgf/cm2程度であるため、ガラス繊維の含有量を20質量%以上にすればよいことがわかる。
ポリアミド66に同ガラス繊維を30質量%配合し、(ポケット隙間/玉径)比が異なる合成樹脂製保持器を作製した。そして、各保持器について荷重最大値を測定した。結果を図6に示すが、ポケット隙間が大きくなるほど荷重最大値が小さくなっているが、(ポケット隙間/玉径)比が2%で最小となり、(ポケット隙間/玉径)比が2%より大きくなるとほぼ飽和、もしくは若干上昇している。このことから、(ポケット隙間/玉径)比の最小値を2%とすればよいことがわかる。
本出願は、2011年8月29日出願の日本特許出願(特願2011-186369)に基づくものであり、その内容はここに参照として取り込まれる。
12 第1の軌道輪
14 第2の軌道輪
15 玉
16 保持器
16a 基部
16b 爪部
17 ポケット
30 油圧式無段変速機
Claims (6)
- 第1の軌道面を有する第1の軌道輪と、第2の軌道面を有する第2の軌道輪と、前記第1の軌道面及び前記第2の軌道面間に転動自在に配置された複数の玉と、前記玉を円周方向に亘って等間隔に保持する保持器とを備えるスラスト軸受において、
前記保持器が合成樹脂製で、かつ、ポケット隙間を玉径の2~5%としたことを特徴とするスラスト軸受。 - 前記保持器が、ガラス繊維を20~40質量%の割合で含有することを特徴とする請求項1記載のスラスト軸受。
- 前記ガラス繊維が異形断面を有することを特徴とする請求項2記載のスラスト軸受。
- 前記保持器の合成樹脂がポリアミドであることを特徴とする請求項1~3の何れか1項に記載のスラスト軸受。
- 前記保持器の合成樹脂が数平均分子量で13000~30000であることを特徴とする請求項1~4の何れか1項に記載のスラスト軸受。
- 前記保持器が射出成形して得られることを特徴とする請求項5記載のスラスト軸受。
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE212012000168.9U DE212012000168U1 (de) | 2011-08-29 | 2012-01-26 | Schublager |
US13/700,344 US8870465B2 (en) | 2011-08-29 | 2012-01-26 | Thrust bearing |
CN2012900000167U CN202971585U (zh) | 2011-08-29 | 2012-01-26 | 推力轴承 |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2011-186369 | 2011-08-29 | ||
JP2011186369 | 2011-08-29 |
Publications (1)
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WO2013031249A1 true WO2013031249A1 (ja) | 2013-03-07 |
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ID=47755775
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Application Number | Title | Priority Date | Filing Date |
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PCT/JP2012/051698 WO2013031249A1 (ja) | 2011-08-29 | 2012-01-26 | スラスト軸受 |
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US (1) | US8870465B2 (ja) |
JP (1) | JP2013064495A (ja) |
CN (1) | CN202971585U (ja) |
DE (1) | DE212012000168U1 (ja) |
WO (1) | WO2013031249A1 (ja) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2016190026A1 (ja) * | 2015-05-22 | 2016-12-01 | Ntn株式会社 | 油圧式無段変速機用スラスト軸受 |
Families Citing this family (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP6421423B2 (ja) * | 2014-03-05 | 2018-11-14 | 株式会社ジェイテクト | スラスト玉軸受用保持器およびスラスト玉軸受 |
CN106104032B (zh) * | 2014-03-17 | 2019-03-29 | 日本精工株式会社 | 推力球轴承用切制保持架及其设计方法、以及具备该保持架的推力球轴承 |
US10436250B2 (en) * | 2015-06-05 | 2019-10-08 | Ntn Corporation | Retainer for thrust bearing and thrust bearing |
JP2019070424A (ja) * | 2017-10-11 | 2019-05-09 | Ntn株式会社 | 転がり軸受 |
DE102018126579A1 (de) * | 2018-10-25 | 2019-04-25 | Schaeffler Technologies AG & Co. KG | Axialwälzlager |
Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2001004003A (ja) * | 1999-06-22 | 2001-01-09 | Nsk Ltd | トロイダル型無段変速機 |
JP2004340290A (ja) * | 2003-05-16 | 2004-12-02 | Ntn Corp | スラスト玉軸受 |
JP2006307900A (ja) * | 2005-04-26 | 2006-11-09 | Nsk Ltd | トロイダル型無段変速機 |
JP2007170465A (ja) * | 2005-12-20 | 2007-07-05 | Nsk Ltd | スラスト玉軸受用加締め保持器及びその設計方法ならびにスラスト玉軸受 |
JP2009097645A (ja) * | 2007-10-17 | 2009-05-07 | Nsk Ltd | アンモニアガスコンプレッサ用転がり軸受 |
JP2011117495A (ja) * | 2009-12-01 | 2011-06-16 | Nsk Ltd | 樹脂製プーリ及び転がり軸受 |
Family Cites Families (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2562911Y2 (ja) * | 1991-07-04 | 1998-02-16 | 光洋精工株式会社 | ストラット用スラスト玉軸受装置 |
US6709161B2 (en) * | 2001-07-31 | 2004-03-23 | Nsk Ltd. | Angular contact ball bearing and spindle device |
JP2003194183A (ja) | 2001-12-27 | 2003-07-09 | Kubota Corp | 静油圧式無段変速装置 |
JP2007170430A (ja) * | 2005-12-19 | 2007-07-05 | Nsk Ltd | ハイブリッド自動車用転がり軸受 |
JP2007177843A (ja) * | 2005-12-27 | 2007-07-12 | Nsk Ltd | 転がり軸受 |
JP2008215566A (ja) * | 2007-03-07 | 2008-09-18 | Nsk Ltd | 油圧無断変速機用スラスト軸受 |
JP2008223970A (ja) * | 2007-03-15 | 2008-09-25 | Nsk Ltd | スラスト軸受用保持器 |
JP2010090364A (ja) * | 2008-09-10 | 2010-04-22 | Ntn Corp | 射出成形体、樹脂製滑り軸受、樹脂製歯車、冠型樹脂製保持器、樹脂製シールおよび転がり軸受 |
KR101280161B1 (ko) * | 2009-12-25 | 2013-06-28 | 닛본 세이고 가부시끼가이샤 | 니들 베어링 |
JP2011186369A (ja) | 2010-03-11 | 2011-09-22 | Toray Ind Inc | 感光性絶縁ペーストおよびそれを用いた多層構造体の製造方法 |
-
2012
- 2012-01-26 CN CN2012900000167U patent/CN202971585U/zh not_active Expired - Fee Related
- 2012-01-26 WO PCT/JP2012/051698 patent/WO2013031249A1/ja active Application Filing
- 2012-01-26 DE DE212012000168.9U patent/DE212012000168U1/de not_active Expired - Lifetime
- 2012-01-26 US US13/700,344 patent/US8870465B2/en active Active
- 2012-08-27 JP JP2012186843A patent/JP2013064495A/ja active Pending
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2001004003A (ja) * | 1999-06-22 | 2001-01-09 | Nsk Ltd | トロイダル型無段変速機 |
JP2004340290A (ja) * | 2003-05-16 | 2004-12-02 | Ntn Corp | スラスト玉軸受 |
JP2006307900A (ja) * | 2005-04-26 | 2006-11-09 | Nsk Ltd | トロイダル型無段変速機 |
JP2007170465A (ja) * | 2005-12-20 | 2007-07-05 | Nsk Ltd | スラスト玉軸受用加締め保持器及びその設計方法ならびにスラスト玉軸受 |
JP2009097645A (ja) * | 2007-10-17 | 2009-05-07 | Nsk Ltd | アンモニアガスコンプレッサ用転がり軸受 |
JP2011117495A (ja) * | 2009-12-01 | 2011-06-16 | Nsk Ltd | 樹脂製プーリ及び転がり軸受 |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2016190026A1 (ja) * | 2015-05-22 | 2016-12-01 | Ntn株式会社 | 油圧式無段変速機用スラスト軸受 |
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CN202971585U (zh) | 2013-06-05 |
JP2013064495A (ja) | 2013-04-11 |
DE212012000168U1 (de) | 2014-04-04 |
US8870465B2 (en) | 2014-10-28 |
US20130114921A1 (en) | 2013-05-09 |
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