WO2011046019A1 - 動力伝達用軸およびアッセンブリ体 - Google Patents
動力伝達用軸およびアッセンブリ体 Download PDFInfo
- Publication number
- WO2011046019A1 WO2011046019A1 PCT/JP2010/066876 JP2010066876W WO2011046019A1 WO 2011046019 A1 WO2011046019 A1 WO 2011046019A1 JP 2010066876 W JP2010066876 W JP 2010066876W WO 2011046019 A1 WO2011046019 A1 WO 2011046019A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- boot
- diameter
- transmission shaft
- power transmission
- male spline
- Prior art date
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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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D1/00—Couplings for rigidly connecting two coaxial shafts or other movable machine elements
- F16D1/10—Quick-acting couplings in which the parts are connected by simply bringing them together axially
- F16D1/108—Quick-acting couplings in which the parts are connected by simply bringing them together axially having retaining means rotating with the coupling and acting by interengaging parts, i.e. positive coupling
- F16D1/116—Quick-acting couplings in which the parts are connected by simply bringing them together axially having retaining means rotating with the coupling and acting by interengaging parts, i.e. positive coupling the interengaging parts including a continuous or interrupted circumferential groove in the surface of one of the coupling parts
-
- 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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D1/00—Couplings for rigidly connecting two coaxial shafts or other movable machine elements
- F16D1/10—Quick-acting couplings in which the parts are connected by simply bringing them together axially
- F16D2001/103—Quick-acting couplings in which the parts are connected by simply bringing them together axially the torque is transmitted via splined connections
-
- 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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
- F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
- F16D3/20—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members
- F16D3/22—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts
- F16D3/223—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts
- F16D2003/22313—Details of the inner part of the core or means for attachment of the core on the shaft
Definitions
- the present invention relates to a power transmission shaft (shaft) and an assembly body used for, for example, a constant velocity universal joint used in a power transmission system of an automobile or various industrial machines.
- the shaft S1 connected to the constant velocity universal joint is generally formed with a male spline 1 at the end and a boot mounted at a position separated from the male spline 1 by a predetermined dimension. Part 2 is formed.
- a boot groove 3 in the circumferential direction is formed in the boot mounting portion 2, and circumferential ridges 4 and 5 are provided at both openings of the boot groove 3.
- a small-diameter portion 6 is provided between the boot mounting portion 2 and the male spline 1. The small diameter portion 6 is provided so that the shaft S1 does not interfere with the outer joint member of the constant velocity universal joint when the constant velocity universal joint takes an operating angle.
- an engaging large-diameter portion 7 that engages with the female spline of the inner ring 11 as an inner joint member of the constant velocity universal joint is provided as described later.
- a tapered portion 8 is provided between the engaging large diameter portion 7 and the small diameter portion 6, and a tapered portion 9 is provided between the small diameter portion 6 and the boot mounting portion 2. Further, a circumferential groove 10 is provided at the end of the male spline 1 (on the side opposite to the boot mounting portion).
- the maximum outer diameter of the male spline 1 is set to D11
- the outer diameter dimension of the engaging large diameter part 7 is set to D12
- the outer diameter dimension of the small diameter part 6 is set to D13
- the maximum of the boot mounting part 2 is set.
- the outer diameter dimension (the outer diameter dimension of the circumferential ridges 4 and 5) is D14
- D13 ⁇ D11 ⁇ D12 ⁇ D14 is set.
- the shaft S1 set in this way is fitted and integrated into an inner ring 11 as an inner joint member of a constant velocity universal joint.
- the inner ring 11 is provided with track grooves 13 disposed on the outer diameter surface 12 thereof at a predetermined pitch along the circumferential direction.
- a female spline 15 is provided on the inner diameter surface of the hole 14 of the inner ring 11.
- the end of the shaft S1 is inserted in the direction of arrow A with respect to the hole 14 of the inner ring 11.
- the male spline 1 at the end of the shaft S1 and the female spline 15 of the inner ring 11 are fitted.
- the shaft S1 is inserted until the large-diameter portion for engagement 7 is engaged with the terminal end (one end edge) of the female spline 15 of the inner ring 11.
- the shaft S 1 is fitted into the hole 14 of the inner ring 11 with the retaining ring 16 fitted in the circumferential groove 10.
- the retaining ring 16 is expanded and the inner ring 11 is expanded in a state in which the diameter is reduced by the female spline 15 and the engaging large diameter portion 7 is engaged with the terminal end of the female spline 15 of the inner ring 11. Will engage with the circumferential cutout 17 provided at the end of the hole 14 (the end corresponding to the inserted tip of the shaft S1).
- the retaining ring 16 restricts the shaft S1 from coming off in the direction of arrow B, and the engaging large diameter portion 7 restricts the pushing of the shaft S1 in the direction of arrow A. Accordingly, the axial displacement of the shaft S1 is eliminated.
- the shaft material diameter when forming such a shaft S1 is determined by the balance between the male spline diameter and the boot groove diameter.
- the diameter and the outer diameter of the engaging large-diameter portion 7 were the maximum diameter portion.
- the shaft shoulder diameter (the large diameter portion for engagement) 7 is the largest. That is, in this case, the material diameter of the shaft S1 is determined by the diameter of the circumferential ridges 4 and 5 of the boot groove 3 or the diameter of the large-diameter portion 7 for engagement, and cannot be smaller than that. For this reason, the material diameter has become relatively large and cost reduction cannot be expected. Even if the circumferential ridges 4 and 5 are not provided, the diameter of the engaging large-diameter portion 7 is used as a reference. In this case, the material diameter is relatively large and low. Cost could not be expected.
- the present invention can reduce the material diameter, suppress the material cost and the turning cost, and realize a low cost, and a power transmission shaft (shaft) and such power transmission.
- An assembly using a shaft is to be provided.
- the outer diameter of the large diameter portion for engagement and the outer diameter of the boot mounting portion is the diameter of the shaft material, and the diameter of the shaft material is maintained. Is smaller than the outer diameter of the male spline at the end. For this reason, compared with the conventional shaft, if the male spline has the same diameter, the diameter of the portion (the large diameter portion for engagement) that becomes the maximum diameter of the material can be reduced. That is, the diameter of the material can be set smaller than the conventional one, and the turning allowance of the boot groove and the male spline can be reduced.
- the male spline is formed by rolling or spline pressing, and the inner diameter of the male spline can be made smaller than the rolling lower diameter or the press lower diameter, and the male spline can be formed larger. For this reason, the outer diameter of the male spline at the end can be set larger than the outer diameter of the large-diameter portion for engagement.
- Material can be medium carbon steel.
- male splines are provided at both ends, and each male spline can be fitted to a female spline of any one of the constant velocity universal joint and the constant velocity universal joint.
- the boot material of the boot mounted on the boot mounting part can be made of resin or rubber.
- resin thermoplastic elastomers such as ester, olefin, urethane, amide, and styrene can be used.
- chloroprene rubber etc. can be used as rubber
- the assembly body of the present invention is an assembly body in which the power transmission shaft and an inner joint member of a constant velocity universal joint are combined, and the male spline at the end of the power transmission shaft is connected to the inner joint member. This is fitted to a female spline provided on the inner diameter surface of the hole.
- the female spline of the inner joint member it is preferable to provide a thin portion at a position corresponding to a portion between the male spline and the large-diameter portion for engagement.
- the material diameter can be reduced, the material cost and turning cost of the shaft can be suppressed, and the cost can be reduced. Since the entire power transmission shaft (shaft) has a shape that is closer to smooth (flat), when heat curing is performed, variation in the depth of the heat-cured layer in the axial direction during heat treatment is reduced, and quality is stabilized. Also, medium carbon steel can be used as a material, and it is not necessary to use a special material, and a power transmission shaft can be provided stably at low cost.
- the male spline is excellent in versatility if it can be fitted to the female spline of either a fixed constant velocity universal joint or a sliding constant velocity universal joint.
- the boots to be used may be made of resin or rubber, and can correspond to boots of various materials.
- the assembly body of the present invention uses the power transmission shaft, the material cost and the turning cost can be suppressed, and the cost can be reduced. Further, if the inner joint member is provided with a thin portion, the weight can be further reduced.
- FIG. 1 shows a power transmission shaft according to the present invention.
- the shaft S is fitted and fixed to an inner ring 41 that is an inner joint member of a constant velocity universal joint.
- a male spline 31 is formed at an end portion of the shaft S.
- a boot mounting portion 32 is formed at a position separated by a predetermined dimension.
- the material of the shaft S is medium carbon steel.
- Carbon steel is an alloy of iron and carbon. Among carbon steels, C content of about 0.3 [mass%] or less is called low carbon steel, about 0.3 to 0.7 [mass%] is called medium carbon steel, and about 0.7 [mass%] or more is called high carbon steel.
- a boot groove 33 in the circumferential direction is formed in the boot mounting portion 32.
- the boot groove 33 in this case does not have a circumferential ridge as in the prior art.
- the boot groove 33 includes a spline-side taper portion 33a, an anti-spline-side arc portion 33c, and a straight portion 33b between the taper portion 33a and the arc portion 33c. Therefore, an edge portion is formed on the anti-spline side of the boot groove 33, and when a boot (not shown) is mounted on the boot mounting portion 32, the edge portion bites into the boot and a stable mounting state can be maintained.
- a small diameter portion 36 is provided between the boot mounting portion 32 and the male spline 31.
- the small diameter portion 36 is provided so that the shaft S does not interfere with the outer joint member of the constant velocity universal joint when the constant velocity universal joint takes an operating angle.
- An engaging large diameter portion 37 is provided between the small diameter portion 36 and the male spline 31.
- a tapered portion 38 is provided between the engaging large diameter portion 37 and the small diameter portion 36, and a tapered portion 39 is provided between the small diameter portion 36 and the boot mounting portion 32.
- a circumferential groove 40 is provided at the end of the male spline 31 (on the side opposite to the boot mounting portion).
- the maximum outer diameter of the male spline 31 is D1
- the outer diameter of the engaging large diameter portion 37 is D2
- the outer diameter of the small diameter portion 36 is D3
- the maximum outer diameter of the boot mounting portion 32 is D4.
- D2 ⁇ D1 and D2 D4. That is, the outer diameters of the engaging large-diameter portion 37 and the boot mounting portion 32 are used as the diameter of the shaft material, and the diameter of the shaft material is kept as it is. Note that D3 ⁇ D2.
- the male spline 31 is formed by rolling or spline pressing, and the inner diameter of the concave line 31a of the male spline 31 is smaller than the lower diameter of the rolled or pressed line, and the convex line 31b of the male spline 31 is formed larger. it can. For this reason, even if the material diameter is smaller than the maximum outer diameter of the male spline 31, when the male spline 31 is formed, the maximum outer diameter of the male spline 31 is the large diameter portion 37 for engagement or the boot mounting portion 32. It can be set larger than the outer diameter.
- the inner ring 41 as an inner joint member of the constant velocity universal joint into which the shaft S is inserted is a track groove disposed on the outer diameter surface 42 at a predetermined pitch along the circumferential direction. 43 is provided.
- a female spline 45 is provided on the inner diameter surface of the hole 44 of the inner ring 41.
- the end of the shaft S is inserted in the direction of arrow A with respect to the hole 44 of the inner ring 41.
- the male spline 31 at the end of the shaft S is fitted into the female spline 45 of the inner ring 41.
- the shaft S is inserted until the large-diameter portion for engagement 37 engages with one tapered end edge 45a of the female spline 45 of the inner ring 41. That is, the end edge 37a on the inner ring hole side of the large-diameter portion 37 for engagement comes into contact with the tapered end edge 45a.
- the shaft S is fitted into the hole 44 of the inner ring 41 with the retaining ring 46 fitted in the circumferential groove 40.
- the retaining ring 46 is restrained so as to be reduced in diameter by the female spline 45, and the retaining ring 16 is expanded in diameter when the large-diameter portion 37 for engagement is engaged with the terminal end of the female spline 45 of the inner ring 41.
- the inner ring 41 is engaged (fitted) with the circumferential notch 47 provided at the end of the hole 44 (the end corresponding to the inserted tip of the shaft S).
- the retaining ring 46 restricts the shaft S from coming off in the arrow B direction, and the engaging large diameter portion 7 restricts the shaft S from being pushed in the arrow A direction. Therefore, the axial displacement of the shaft S1 can be eliminated.
- a male spline 31 and a boot mounting portion 32 as shown in FIG. 1 are also formed at the opposite end (not shown).
- Boots (not shown) mounted on the boot mounting portion 32 can be made of a resin or rubber as the boot material.
- the resin thermoplastic elastomers such as ester, olefin, urethane, amide, and styrene can be used.
- chloroprene rubber etc. can be used as rubber
- the outer diameter of the engaging large-diameter portion 37 and the boot mounting portion 32 is used as the diameter of the shaft material, and the diameter of the shaft material is maintained.
- the outer diameter of the male spline 31 is smaller.
- the diameter of the portion (the large diameter portion for engagement) that becomes the maximum diameter of the material can be reduced. That is, the diameter of the material can be set smaller than the conventional one, and the turning allowance of the boot groove and the male spline can be reduced. Thereby, the material cost and turning cost of the shaft can be suppressed, and the cost can be reduced.
- the entire power transmission shaft (shaft) has a shape that is closer to smooth (flat), when heat curing is performed, variation in the depth of the heat-cured layer in the axial direction during heat treatment is reduced, and quality is stabilized.
- medium carbon steel can be used as a material, and it is not necessary to use a special material, and a power transmission shaft can be provided stably at low cost.
- the shaft (power transmission shaft) S of the male spline 31 can be fitted to the female spline of either a fixed constant velocity universal joint or a sliding constant velocity universal joint. For this reason, the power transmission shaft S is excellent in versatility.
- the boots to be used may be made of resin or rubber, and can correspond to boots of various materials.
- the assembly body of the present invention uses the power transmission shaft, the material cost and the turning cost can be suppressed, and the cost can be reduced.
- FIG. 3 shows a modified example of the inner ring 41.
- the female spline 45 that is, in the ridge 50 of the female spline 45
- a portion (small diameter portion) 55 between the male spline 31 and the large diameter portion 37 is provided in the female spline 45.
- a dull portion (notch portion) 56 is provided at a corresponding position. That is, at the position corresponding to the portion 55, it is not necessary to perform spline fitting, and thus the thin portion 56 can be formed.
- the constant velocity universal joint is a fixed constant velocity universal joint.
- a sliding type constant velocity universal joint may be used, and the fixed type constant velocity universal joint can be used for various types such as a Rzeppa type and an undercut free type, and a sliding type constant velocity universal joint.
- a joint it can use for various types, such as a double offset type, a tripod type, and a cross groove type.
- the power transmission shaft (shaft) may be solid or hollow.
- the medium-coal-layer steel is used in the embodiment, but it may be a low-carbon steel or a high-coal-layer steel. That is, in such a shaft, steel is generally used, but a composite material such as an alloy or carbon may be used. Further, it is preferable to subject the surface to a thermosetting treatment. Various heat treatments such as induction hardening and carburizing and quenching can be employed as the thermosetting treatment.
- induction hardening is a hardening method that applies the principle of heating a conductive object by placing Joule heat in a coil through which high-frequency current flows, and generating Joule heat by electromagnetic induction. is there.
- carburizing and quenching is a method in which carbon is infiltrated / diffused from the surface of a low carbon material and then quenched.
- the power transmission shaft (shaft) is used for, for example, a constant velocity universal joint used in power transmission systems of automobiles and various industrial machines.
- the assembly body may be a combination of a power transmission shaft and a constant velocity universal joint.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
- Sealing Devices (AREA)
Abstract
Description
32 ブーツ装着部
33 ブーツ溝
37 係合用大径部
45 雌スプライン
55 部位
56 ぬすみ部
Claims (8)
- 端部の雄スプラインと、この雄スプラインが他部材の雌スプラインに嵌合された状態で、軸方向の押し込みを規制する係合用大径部と、ブーツ装着用のブーツ溝とを有する動力伝達用軸であって、
前記係合用大径部の外径寸法をD2とし、前記雄スプラインの最大外径寸法をD1とし、前記ブーツ溝が設けられたブーツ装着部の外径寸法をD4としたときに、D2<D1とするとともに、D2=D4とし、かつ、前記係合用大径部及びブーツ装着部の外径をシャフト素材の径として、そのシャフト素材の径のままとしたことを特徴とする動力伝達用軸。 - 材質を中炭素鋼としたことを特徴とする請求項1に記載の動力伝達用軸。
- 雄スプラインを転造加工又はプレス加工にて仕上げたことを特徴とする請求項1又は請求項2に記載の動力伝達用軸。
- 雄スプラインが両端部に設けられ、各雄スプラインは、固定式等速自在継手と摺動式等速自在継手とのいずれの等速自在継手の雌スプラインにも嵌合可能であることを特徴とする請求項1~請求項3のいずれか1項に記載の動力伝達用軸。
- 前記ブーツ装着部に装着されるブーツのブーツ材料を樹脂としたことを特徴とする請求項1~請求項4のいずれか1項に記載の動力伝達用軸。
- 前記ブーツ装着部に装着されるブーツのブーツ材料をゴムとしたことを特徴とする請求項1~請求項4のいずれか1項に記載の動力伝達用軸。
- 前記請求項1~請求項6のいずれか1項に記載の動力伝達用軸と、等速自在継手の内側継手部材とが組み合わされてなるアッセンブリ体であって、動力伝達用軸の端部の雄スプラインを、前記内側継手部材の孔部の内径面に設けられた雌スプラインに嵌合させたことを特徴とするアッセンブリ体。
- 前記内側継手部材の雌スプラインにおいて、雄スプラインと係合用大径部との間の部位に対応する位置にぬすみ部を設けたことを特徴とする請求項7に記載のアッセンブリ体。
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CN201080046266XA CN102575718A (zh) | 2009-10-13 | 2010-09-29 | 动力传递用轴及装配体 |
US13/394,571 US20120172137A1 (en) | 2009-10-13 | 2010-09-29 | Power-transmission shaft and assembly |
EP10823287A EP2489893A1 (en) | 2009-10-13 | 2010-09-29 | Power-transmission shaft and assembly |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2009236117A JP2011085152A (ja) | 2009-10-13 | 2009-10-13 | 動力伝達用軸およびアッセンブリ体 |
JP2009-236117 | 2009-10-13 |
Publications (1)
Publication Number | Publication Date |
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WO2011046019A1 true WO2011046019A1 (ja) | 2011-04-21 |
Family
ID=43876072
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2010/066876 WO2011046019A1 (ja) | 2009-10-13 | 2010-09-29 | 動力伝達用軸およびアッセンブリ体 |
Country Status (5)
Country | Link |
---|---|
US (1) | US20120172137A1 (ja) |
EP (1) | EP2489893A1 (ja) |
JP (1) | JP2011085152A (ja) |
CN (1) | CN102575718A (ja) |
WO (1) | WO2011046019A1 (ja) |
Families Citing this family (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2014156640A1 (ja) * | 2013-03-25 | 2014-10-02 | Ntn株式会社 | 動力伝達軸およびスプライン加工方法 |
CN105473882B (zh) * | 2013-07-30 | 2018-10-12 | 日本精工株式会社 | 带有万向接头用叉轭的力矩传递轴及其制造方法和伸缩轴 |
US11125277B2 (en) | 2017-07-19 | 2021-09-21 | Zhejiang CFMOTO Power Co., Ltd. | Type of constant velocity universal joint with the spline slip structure |
US11242896B2 (en) * | 2017-07-19 | 2022-02-08 | Zhejiang Cfmoto Power Co. Ltd. | Spline slip constant velocity joint |
JP6533860B1 (ja) * | 2018-12-04 | 2019-06-19 | 株式会社ショーワ | 推進軸 |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2005344746A (ja) * | 2004-05-31 | 2005-12-15 | Toyoda Mach Works Ltd | ドライブシャフト |
JP2007232043A (ja) * | 2006-02-28 | 2007-09-13 | Ntn Corp | ブーツ取付構造 |
JP3977975B2 (ja) | 2000-01-25 | 2007-09-19 | Ntn株式会社 | 等速自在継手 |
JP2007292170A (ja) * | 2006-04-24 | 2007-11-08 | Ntn Corp | 動力伝達軸及びその製造方法 |
Family Cites Families (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3326990A1 (de) * | 1983-07-27 | 1985-02-07 | Dr.Ing.H.C. F. Porsche Ag, 7000 Stuttgart | Vorrichtung zum einstellen von gelenkwellen |
EP1016801B1 (en) * | 1998-07-22 | 2003-09-10 | Ntn Corporation | Power transmission mechanism |
JP2005146313A (ja) * | 2003-11-12 | 2005-06-09 | Ntn Corp | 動力伝達軸 |
US7419433B2 (en) * | 2004-05-24 | 2008-09-02 | Ntn Corporation | ATV drive shaft and constant velocity joint |
JP4979938B2 (ja) * | 2005-12-26 | 2012-07-18 | Ntn株式会社 | 等速自在継手及びその内方部材 |
EP2175177B1 (en) * | 2007-07-31 | 2015-11-04 | NTN Corporation | Boot fixing method |
-
2009
- 2009-10-13 JP JP2009236117A patent/JP2011085152A/ja not_active Withdrawn
-
2010
- 2010-09-29 US US13/394,571 patent/US20120172137A1/en not_active Abandoned
- 2010-09-29 EP EP10823287A patent/EP2489893A1/en not_active Withdrawn
- 2010-09-29 CN CN201080046266XA patent/CN102575718A/zh active Pending
- 2010-09-29 WO PCT/JP2010/066876 patent/WO2011046019A1/ja active Application Filing
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP3977975B2 (ja) | 2000-01-25 | 2007-09-19 | Ntn株式会社 | 等速自在継手 |
JP2005344746A (ja) * | 2004-05-31 | 2005-12-15 | Toyoda Mach Works Ltd | ドライブシャフト |
JP2007232043A (ja) * | 2006-02-28 | 2007-09-13 | Ntn Corp | ブーツ取付構造 |
JP2007292170A (ja) * | 2006-04-24 | 2007-11-08 | Ntn Corp | 動力伝達軸及びその製造方法 |
Also Published As
Publication number | Publication date |
---|---|
JP2011085152A (ja) | 2011-04-28 |
CN102575718A (zh) | 2012-07-11 |
US20120172137A1 (en) | 2012-07-05 |
EP2489893A1 (en) | 2012-08-22 |
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