WO2005033538A1 - 固定式等速自在継手 - Google Patents
固定式等速自在継手 Download PDFInfo
- Publication number
- WO2005033538A1 WO2005033538A1 PCT/JP2004/014538 JP2004014538W WO2005033538A1 WO 2005033538 A1 WO2005033538 A1 WO 2005033538A1 JP 2004014538 W JP2004014538 W JP 2004014538W WO 2005033538 A1 WO2005033538 A1 WO 2005033538A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- cage
- track
- constant velocity
- clearance
- inner ring
- Prior art date
Links
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
- 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
- F16D3/224—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 the groove centre-lines in each coupling part lying on a sphere
- F16D3/2245—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 the groove centre-lines in each coupling part lying on a sphere where the groove centres are offset from the joint centre
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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
- 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
- F16D2003/22303—Details of ball cages
-
- 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
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10S464/00—Rotary shafts, gudgeons, housings, and flexible couplings for rotary shafts
- Y10S464/904—Homokinetic coupling
- Y10S464/906—Torque transmitted via radially spaced balls
Definitions
- the present invention relates to a fixed type constant velocity universal joint, and relates to a driving shaft, a propeller shaft, other automobiles, and various industrial machines in addition to various steering devices including an electric power steering. It can be used for transmission systems.
- Background Art In general, a plurality of cardan joints (cross-shaft joints) have been used in automobile steering devices.
- a cardan joint is a non-constant universal joint whose rotational fluctuation increases between the input shaft and the output shaft when the operating angle increases, and it is necessary to ensure constant speed by combining multiple cardan joints. There is a problem that the degree of freedom of design is impaired.
- the fixed type constant velocity universal joint consists of an outer ring having a plurality of curved track grooves on the spherical inner surface, an inner ring having a plurality of curved track grooves on the spherical outer surface, and a torque incorporated between the track grooves of the outer ring and the inner ring. It consists of a transmission pole and a cage that holds the torque transmission ball.
- the center of curvature of the outer ring track groove (outer ring track center) is relative to the center of curvature of the spherical inner surface of the outer ring, and the center of curvature of the inner ring track groove (inner ring track center) is relative to the center of curvature of the inner ring spherical outer surface.
- the pole track which is composed of the outer ring track groove and the inner ring track groove, has a wedge shape that expands toward the opening side of the outer ring. It has become.
- the rotational backlash is eliminated or suppressed by clogging the track clearance by the preload means provided inside the joint.
- a fixed constant velocity universal joint has been proposed.
- the pole track has a wedge shape that expands toward the outer ring opening side.
- the cage is provided with a pressing part on the inner ring side that applies an elastic pressing force in the axial direction and a receiving part that receives the pressing force from the pressing part. To do.
- the inner ring is pressed toward the opening side of the outer ring, and an axial relative movement occurs between the two.
- This relative movement reduces the track clearance through the poles and prevents the occurrence of rotating backlash.
- the axial clearance generated by the track clearance may not be able to be filled. It becomes difficult to prevent the occurrence of this.
- a fixed type constant velocity universal joint includes an outer member having an inner diameter surface formed with a plurality of track grooves, and an outer diameter surface formed with a plurality of track grooves.
- the axial clearance between the inner member and the cage is larger than the axial clearance generated by the track clearance, including the state where the joint has an operating angle, and the axial clearance between the inner member and the cage is tracked. It is characterized by 2.5 to 6.5 times the radial clearance.
- the axial clearance between the inner member and the cage is smaller than the axial clearance due to the radial clearance of the track, including the state where the operating angle is closed. Since the inner ring and the cage previously contacted each other, there is a limit to reducing the axial clearance due to the radial clearance of the track. Therefore, the axial clearance between the inner member and the cage needs to be larger than the axial clearance generated by the track clearance, including the state where the joint has a working angle.
- the axial clearance between the inner member and the cage is set to 2.5 to 6.5 times the radial clearance of the track. Accordingly, the inner member is pressed toward the opening side of the outer member due to the elastic contact between the pressing portion and the receiving portion, and relative movement in the axial direction occurs between the two members.
- the clearance in the rotational direction of can be reliably packed.
- a chamfered portion that interferes with the inner diameter surface of the cage is formed on the outer diameter surface of the inner member, or the inner diameter surface of the cage is prevented from interfering with the outer diameter surface of the inner member.
- An aspherical shape is desirable.
- the cage and the inner member move relative to each other, it is possible to prevent interference between the cage and the inner member.
- the inner member is pressed toward the opening side of the outer member by the elastic contact between the pressing portion and the receiving portion of the preload mechanism, and relative movement in the axial direction occurs between the two,
- the axial clearance generated by the track clearance is completely reduced. Since the inner space and the cage do not come into contact with each other before being installed, the track clearance is reliably filled via the balls, so that it is possible to reliably prevent the occurrence of rotating backlash, and it is a high-quality automotive shaft coupling.
- the fixed type constant velocity universal joint includes an outer ring having an inner spherical surface formed with a plurality of track grooves, and an inner ring having an outer spherical surface formed with a plurality of track grooves, A wedge-shaped pole track that is reduced from one axial direction to the other in the axial direction of the joint formed by a pair of track grooves on the outer ring and track grooves on the inner ring, and a torque transmission pole that is incorporated in each pole track.
- a cage having a pocket for holding the torque transmission pole and interposed between the inner spherical surface of the outer ring and the outer spherical surface of the inner ring, and connecting the center of curvature of the track groove of the outer ring and the center of curvature of the track groove of the inner ring.
- the center position in the axial direction of the cage pocket is offset from the center of curvature of the cage to the center of curvature of the track groove of the outer ring. Is characterized in that the shifted.
- the amount of shift in the axial center position of the pocket should be such that the clearance between the inner ring and the cage can be secured to reduce the track clearance by preload.
- the shift amount of the center position of the pocket in the axial direction is set to 1.0% to 3.0% of the offset amount of the track groove.
- the inner ring and the cage will interfere with each other on the inner side of the outer ring during cross operation. On the other hand, if it is too large, the inner ring and the cage interfere with each other before the track groove and the torque transmission ball come into contact with each other when there is no load. If the spherical clearance is too large in advance, the amount of twist when torque is applied increases, which is not preferable.
- the difference between the axial dimension of the cage pocket and the diameter of the torque transmitting pole is preferably in the range of 0 to 3 O jU m. The positive clearance setting is good to reduce the resistance value. However, if the clearance is too large, the behavior of the torque transmission ball cannot be suppressed and it will not operate smoothly.
- FIG. 1 is a longitudinal sectional view of a fixed type constant velocity universal joint, which shows one embodiment of the present invention.
- FIG. 2 is a partially enlarged view of the joint of FIG.
- FIG. 3 is a longitudinal sectional view showing a modified example of the inner ring.
- FIG. 4 is a longitudinal sectional view showing a modified example of the inner ring.
- FIG. 5 is a longitudinal sectional view showing a modified example of the inner ring.
- FIG. 6 is a longitudinal sectional view showing a modified example of the inner ring.
- FIG. 7 is a longitudinal sectional view showing a modified example of the inner ring.
- FIG. 8 is a longitudinal sectional view showing a modified example of the inner ring.
- FIG. 9 is a longitudinal sectional view showing a modified example of the inner ring.
- FIG. 10 is a longitudinal sectional view showing a modified example of the inner ring.
- FIG. 11 is a longitudinal sectional view showing a modified example of the inner ring.
- FIG. 12 is a longitudinal sectional view showing a modified example of the inner ring.
- FIG. 13 is a longitudinal sectional view showing a modified example of the inner ring.
- FIG. 14 is a longitudinal sectional view showing a modified example of the cage.
- FIG. 15 is a longitudinal sectional view showing a modified example of the cage.
- FIG. 16 is a partial longitudinal sectional view of a fixed type constant velocity universal joint showing the prior art.
- FIG. 17 is a longitudinal sectional view showing a state of the joint of FIG.
- FIG. 18 is an enlarged view of a portion surrounded by a two-dot chain line in FIG.
- FIG. 19 is a partially enlarged view of the fixed type constant velocity universal joint shown in FIG. 1, and shows another embodiment of the present invention.
- FIG. 20 is a partially enlarged view of FIG. 19 corresponding to FIG.
- FIG. 21 is a schematic plan view of the steering device.
- FIG. 22 is a schematic side view of the steering device.
- BEST MODE FOR CARRYING OUT THE INVENTION is a schematic side view of the steering device.
- BJ Tsuba type
- UJ undercut free type
- the fixed type constant velocity universal joint has an outer ring 1, an inner ring 2, a plurality of torque transmission balls 3 and a cage 4 as main components.
- the outer ring 1 has an inner spherical surface 1 b, and a track groove 1 a extending in the axial direction is formed on the inner spherical surface 1 b.
- the inner ring 2 has an outer spherical surface 2b, and a track groove 2a extending in the axial direction is formed on the outer spherical surface 2b.
- the inner ring 2 and the shaft 5 constitute an inner member 6 by coupling the inner ring 2 to the shaft 5 via torque transmission means such as a selection or a spline.
- the track groove 1a of the outer ring 1 and the track groove 2a of the inner ring 2 are paired to form a pole track, and one torque transmission ball 3 is incorporated in each ball track.
- the cage 4 is interposed between the inner spherical surface 1 b of the outer ring 1 and the outer spherical surface 2 b of the inner ring 2 and has pockets 4 a for accommodating the torque transmission poles 3 at equal intervals in the circumferential direction. .
- the number of track grooves 1 a and 2 a is six, for example, but there are cases where there are three or eight and there is no particular limitation.
- the track grooves 1 a and 2 a are circular when viewed in the longitudinal section (Fig. 1), and the center of curvature of the track groove 1 a of the outer ring 1 (outer ring track center) is relative to the center of curvature O of the inner spherical surface of the outer ring 1.
- the center of curvature of the track groove 2a of the inner ring 2 (inner The wheel track center) 0 2 is offset from the center of curvature O of the outer spherical surface 2 b of the inner ring 2 by an equal distance in the axial direction. Therefore, the pole track formed by the pair of track grooves 1 a and 2 a has a wedge shape that decreases from the opening side of the outer ring 1 toward the back side.
- the center of curvature of the inner spherical surface 1 b of the outer ring 1 and the center of curvature of the outer spherical surface 4 b of the cage 4 are equal to the joint center O.
- the center of curvature of the outer spherical surface 2 b of the inner ring 2 and the center of curvature of the inner spherical surface 4 c of the cage 4 also coincide with the joint center O. Therefore, the offset amount of the outer ring track center 0 is the distance from the joint center O to the outer ring track center, and the offset amount of the inner ring track center o 2 is the distance from the joint center o to the inner ring track center 0 2. equal.
- a pressing member 10 is provided at the shaft end of the shaft 5.
- the pressing member 10 in the illustrated example includes a pole as the pressing portion 11, a compression coil spring as the elastic member 12, and a case 13 for using the pressing portion 11 and the elastic member 12 as an assembly.
- the elastic member 1 2 acts as an elastic force through the pressing portion 11.
- the case 13 is fixed to the front end portion of the shaft 5 integrated with the inner joint member 2 by a selection coupling by an appropriate means such as press-fitting or a bonding material.
- a receiving member 14 is attached to the end of the cage 4 on the back side of the outer ring.
- the receiving member 14 is a lid that covers the end opening of the cage 4 on the back side of the outer ring, and is composed of a spherical part 14 a that is partially spherical and a mounting part 14 b that is formed annularly on the outer periphery thereof.
- the Spherical section 1 4 a The inner surface (the surface facing the shaft 5) has a concave spherical shape, and this concave spherical portion functions as a receiving portion 15 that receives the pressing force from the pressing portion 11.
- the mounting portion 14 b is fixed to the end portion of the cage 4 by appropriate means such as press-fitting and welding.
- the pressing part 11 is provided on the inner ring side and the receiving part 15 is provided on the cage side.
- the pressing part is provided on the cage side and the receiving part is provided on the inner ring side.
- a built-in structure is also possible.
- the inner ring Set the axial clearance between 2 and cage 4 to 2.5 to 6.5 times the radial clearance due to track clearance.
- the magnification i.e., 2.5 to 6.5 fold range, the axial distance (track offset amount) from the joint center O to outer race track center 0 ,, inner track center 0 2 and is obtained from the track PCD.
- the track PCD means the track groove center diameter of the outer ring 1 and the inner ring 1.
- the track grooves 1 a and 2 a of the outer ring 1 and the inner ring 2 are It becomes difficult to secure the necessary depth to transmit the torque, and conversely, if it is larger than 6.5 times, it will be bent when the operating angle is set between the input and output shafts of the constant velocity universal joint. It causes deterioration of operability. Therefore, it is desirable to set the axial clearance between the inner ring and the cage to 2.5-6.5 times the radial clearance caused by the track clearance.
- a chamfered portion that forms an interference with the inner spherical surface 4 c of the cage 4 is formed on the outer spherical surface 2 b of the inner ring 2. Further, the inner spherical surface 4 c of the cage 4 is formed into an aspherical shape that suppresses interference with the outer spherical surface of the inner ring 2. As a result, the inner ring 2 moves smoothly with respect to the cage 4, and the amount of movement of the inner ring 2 due to the preload can be secured and the track clearance can be more reliably packed.
- FIGS. 2 to 7 are conceivable as the form of forming the chamfered portion on the outer spherical surface 2 b of the inner ring 2.
- FIG. 2 shows the case where a taper-shaped chamfered portion (the broken line in the figure shows the conventional shape) is formed on the outer ring opening side edge of the outer spherical surface 2b of the inner ring 2.
- Figs. Chamfered portion m 2 to m 6 (curved line in the figure) with a curved center of curvature 0 3 to 0 7 offset from the joint center O in the radial direction at the outer ring opening side edge of the outer spherical surface 2b
- Each part shows a conventional shape).
- the tapered chamfer tr ⁇ in FIG. 2 has a predetermined inclination angle from the end face of the inner ring 2. Cut edge m 2 - m 6 in FIGS.
- FIG. 8 shows the case where a taper-shaped chamfered portion ⁇ 'is formed at the outer ring inner edge of the outer ring 2 b of the inner ring 2.
- Fig. 9 to Fig. 13 consist of a curved surface with a center of curvature ⁇ ⁇ 0 7 ′ offset from the joint center O in the radial direction in the axial direction at the outer ring inner side edge of the outer sphere 2 b of the inner ring 2
- a case where chamfered portions m 2 ′ to m 6 ′ are formed is shown.
- the taper-shaped chamfered portion rr ⁇ ′ in FIG. 8 has a predetermined angle of inclination from the end surface of the inner ring 2.
- the chamfers m to m 6 'in Fig. 9 to Fig. 13 are the centers of curvature O to O offset from the joint center O in the axial direction to the radial direction (in Fig. 12 including the tilt angle ⁇ direction from the joint center O).
- the configuration in which the inner spherical surface 4 c of the cage 4 is formed into an aspherical shape that suppresses interference with the outer spherical surface of the inner ring 2 those shown in FIGS. 14 and 15 are conceivable.
- FIG. 14 shows the center of curvature where the flat part p is formed at the joint center O of the inner spherical surface 4c 'of the cage 4 and both sides of the flat part P are offset in the axial and radial directions from the joint center O.
- Fig. 15 shows the center of curvature obtained by offsetting the inner spherical surface 4 c ′ of the cage 4 from the joint center O in the radial direction.
- Each case is shown as a concave spherical surface with radius R ''.
- the elastic contact between the pressing portion 1 1 and the receiving portion 15 can be achieved.
- the inner ring 2 is pressed toward the opening side of the outer ring 1 and a relative movement in the axial direction occurs between the two, so that the cage clearance does not interfere with the inner ring 2 even when the joint has an operating angle. Since the inner ring 2 can move in the axial direction until it is fully packed, the track clearance is securely packed, and when the cross is operated, the torque transmission ball 3 stabilizes the cage 4 and controls it to the 0 Z 2 deg position.
- the radial clearance of the truck is 0 to 1.5% with respect to the truck PCD, and the radial clearance between the outer ring 1 and the cage 4 is 0 with respect to the truck PCD. It is desirable to make it 1.7%.
- the axial clearance between the inner ring 2 and the cage 4 also needs to be increased in order to reduce backlash.
- the inner ring 2 moves toward the inner side of the outer ring 1 due to the shape of the pole track.
- the outer spherical surface 2 b of the inner ring 2 and the receiving member 1 4 before the outer spherical surface 2 b of the inner ring 2 abuts the inner spherical surface 4 c of the cage. Will interfere with the inner concave spherical surface of the partial spherical surface 14a.
- the fixing position of the receiving member 14 and the cage 4 is set to the rear side of the outer ring 1, or the mounting portion 14b of the receiving member 14 is enlarged and the partial spherical surface of the receiving member 14 is 1 4 It is necessary to enlarge the inner concave sphere of a.
- the cage outer spherical surface is used to compensate for the decrease in strength due to the cage 4 thickness reduction or the aforementioned cage thickness reduction.
- the ratio of the track PCD to the torque transmission pole diameter is desirably 1.5 to 4.0 times. If this ratio is less than 1.5, the strength of the inner ring 2 is reduced. Conversely, if the ratio is greater than 4.0, not only the strength of the cage 4 is lowered but also the outer diameter of the outer ring 1 is increased.
- the inner ring 2 is pushed into the inner side of the outer ring 1 (inner ring track center 0 2 side).
- the outer spherical surface 2 b of the inner ring 2 and the inner spherical surface 4 c of the cage 4 interfere with each other and appear as a hook when the cross is operated.
- tilt-up and tilt-down operations cannot be performed smoothly in tilt steering, and in some cases, the operation may become impossible.
- the pocket 4a of the cage 4 is basically located at the inner and outer spherical surfaces of the cage 4 except when the contact portion between the pocket 4a and the torque transmitting ball 3 is not secured at a high angle.
- the center of the inner and outer spherical surfaces 4 b and 4 c of cage 4 and the position of pocket 4 a The diameter was half of d (d Z2). Therefore, the radial clearance between the inner ring 2 and the cage 4 is (spherical clearance) 2.
- Fig. 20 is a diagram corresponding to Fig. 18 showing the prior art. As is clear from the comparison of both figures, in the case of Fig.
- FIG. 20 shows examples of steering devices. This steering device converts the rotational movement of the steering wheel 21 into the reciprocating movement of the tie rod 24 by transmitting it to the steering gear 23 via a steering column consisting of one or more steering shafts 22. It is what you do.
- the steering device may be an electric power steering device (EPS) that applies an assisting force by a motor or a hydraulic power steering device.
- EPS electric power steering device
Description
Claims
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US10/572,280 US7704149B2 (en) | 2003-10-01 | 2004-09-27 | Fixed type constant velocity joint |
EP04773567A EP1669622B1 (en) | 2003-10-01 | 2004-09-27 | Fixed type constant velocity universal joint |
DE602004030359T DE602004030359D1 (de) | 2003-10-01 | 2004-09-27 | Homokinetisches universalfestgelenk |
AT04773567T ATE490417T1 (de) | 2003-10-01 | 2004-09-27 | Homokinetisches universalfestgelenk |
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2003-343173 | 2003-10-01 | ||
JP2003343173A JP4554181B2 (ja) | 2003-10-01 | 2003-10-01 | 固定型等速自在継手 |
JP2004-031130 | 2004-02-06 | ||
JP2004031130A JP4712304B2 (ja) | 2004-02-06 | 2004-02-06 | 固定式等速自在継手 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2005033538A1 true WO2005033538A1 (ja) | 2005-04-14 |
Family
ID=34425329
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2004/014538 WO2005033538A1 (ja) | 2003-10-01 | 2004-09-27 | 固定式等速自在継手 |
Country Status (5)
Country | Link |
---|---|
US (1) | US7704149B2 (ja) |
EP (2) | EP1669622B1 (ja) |
AT (2) | ATE511613T1 (ja) |
DE (1) | DE602004030359D1 (ja) |
WO (1) | WO2005033538A1 (ja) |
Families Citing this family (13)
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CN101321964A (zh) * | 2005-09-23 | 2008-12-10 | Gkn动力传动系统国际有限责任公司 | 优化的具有无凹槽球道的同步刚性万向节 |
JP4959177B2 (ja) | 2005-11-18 | 2012-06-20 | Ntn株式会社 | 固定式等速自在継手 |
JP5183930B2 (ja) * | 2007-02-02 | 2013-04-17 | Ntn株式会社 | 固定式等速自在継手 |
JP5143453B2 (ja) * | 2007-03-20 | 2013-02-13 | Ntn株式会社 | 等速自在継手 |
DE102009032781A1 (de) | 2009-07-10 | 2011-01-27 | Neumayer Tekfor Holding Gmbh | Käfig für Kugelgelenk und Kugelgelenk |
US8317630B1 (en) * | 2011-07-06 | 2012-11-27 | Dana Automotive Systems Group, Llc | Plunging type constant velocity joint |
JP5840463B2 (ja) | 2011-11-10 | 2016-01-06 | Ntn株式会社 | 固定式等速自在継手 |
JP6114644B2 (ja) * | 2013-06-26 | 2017-04-12 | Ntn株式会社 | 固定式等速自在継手 |
WO2015153431A2 (en) | 2014-04-04 | 2015-10-08 | Dana Automotive Systems Group, Llc | Constant velocity joint assembly |
CN108700124B (zh) | 2016-02-10 | 2021-09-28 | 德纳汽车系统集团有限责任公司 | 直接小齿轮安装的恒定速度接头 |
EP3455514B1 (en) | 2016-05-10 | 2020-04-08 | Dana Automotive Systems Group, LLC | Boot assembly for a constant velocity joint |
JP2020512515A (ja) | 2017-03-31 | 2020-04-23 | デーナ、オータモウティヴ、システィムズ、グループ、エルエルシー | 等速ジョイントアセンブリ |
DE102017210135B4 (de) * | 2017-06-16 | 2021-02-11 | Volkswagen Aktiengesellschaft | Kugelkäfig für VL- und CG-Gelenke |
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JPH0942304A (ja) * | 1995-07-28 | 1997-02-10 | Ntn Corp | 等速自在継手 |
JP2003130082A (ja) * | 2001-10-26 | 2003-05-08 | Ntn Corp | 固定型等速自在継手 |
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JPS6039897B2 (ja) * | 1978-12-04 | 1985-09-07 | エヌ・テ−・エヌ東洋ベアリング株式会社 | 等速ジヨイント |
JPS5754723A (en) * | 1980-09-18 | 1982-04-01 | Toyota Motor Corp | Synchronized ball joint |
US4410279A (en) | 1981-03-31 | 1983-10-18 | British Nuclear Fuels Limited | Apparatus for agitating the contents of storage tanks |
JPS6239025A (ja) | 1985-08-14 | 1987-02-20 | Fujitsu Ltd | 半導体装置の製造方法 |
JPH0799176B2 (ja) * | 1989-07-17 | 1995-10-25 | エヌティエヌ株式会社 | 等速自在継手 |
IT1268212B1 (it) * | 1993-12-17 | 1997-02-21 | Gkn Automotive Ag | Giunto girevole omocinetico a sfere |
JPH07301246A (ja) * | 1994-05-06 | 1995-11-14 | Unisia Jecs Corp | 等速ジョイント |
JPH08121491A (ja) * | 1994-10-24 | 1996-05-14 | Koyo Seiko Co Ltd | 自在継手 |
JPH08189533A (ja) * | 1995-01-12 | 1996-07-23 | Honda Motor Co Ltd | 等速自在継手 |
JPH09291945A (ja) | 1996-04-26 | 1997-11-11 | Ntn Corp | 固定式等速ジョイント |
JP3570811B2 (ja) * | 1996-02-14 | 2004-09-29 | Ntn株式会社 | 自動車の動力伝達装置およびその等速自在継手 |
DE19802587C1 (de) * | 1998-01-23 | 1999-07-01 | Gkn Loebro Gmbh | Gleichlaufgelenk |
US20030054893A1 (en) * | 2001-09-20 | 2003-03-20 | Delphi Technologies Inc. | Constant velocity joint |
-
2004
- 2004-09-27 EP EP04773567A patent/EP1669622B1/en not_active Not-in-force
- 2004-09-27 WO PCT/JP2004/014538 patent/WO2005033538A1/ja active Application Filing
- 2004-09-27 AT AT10007894T patent/ATE511613T1/de not_active IP Right Cessation
- 2004-09-27 AT AT04773567T patent/ATE490417T1/de not_active IP Right Cessation
- 2004-09-27 US US10/572,280 patent/US7704149B2/en not_active Expired - Fee Related
- 2004-09-27 DE DE602004030359T patent/DE602004030359D1/de active Active
- 2004-09-27 EP EP10007894A patent/EP2239478B1/en active Active
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5773228A (en) * | 1980-10-27 | 1982-05-07 | Toyota Motor Corp | Bar field uniform joint |
JPS57171427U (ja) * | 1981-04-23 | 1982-10-28 | ||
JPS6239025U (ja) * | 1985-08-29 | 1987-03-09 | ||
GB2269438A (en) * | 1992-08-08 | 1994-02-09 | Gen Motors France | Constant velocity joint |
JPH0942304A (ja) * | 1995-07-28 | 1997-02-10 | Ntn Corp | 等速自在継手 |
JP2003130082A (ja) * | 2001-10-26 | 2003-05-08 | Ntn Corp | 固定型等速自在継手 |
Also Published As
Publication number | Publication date |
---|---|
ATE511613T1 (de) | 2011-06-15 |
EP1669622B1 (en) | 2010-12-01 |
EP1669622A4 (en) | 2008-12-03 |
EP1669622A1 (en) | 2006-06-14 |
EP2239478A1 (en) | 2010-10-13 |
US20080096678A1 (en) | 2008-04-24 |
ATE490417T1 (de) | 2010-12-15 |
DE602004030359D1 (de) | 2011-01-13 |
EP2239478B1 (en) | 2011-06-01 |
US7704149B2 (en) | 2010-04-27 |
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