WO2005068863A1 - 等速ジョイント - Google Patents
等速ジョイント Download PDFInfo
- Publication number
- WO2005068863A1 WO2005068863A1 PCT/JP2005/000317 JP2005000317W WO2005068863A1 WO 2005068863 A1 WO2005068863 A1 WO 2005068863A1 JP 2005000317 W JP2005000317 W JP 2005000317W WO 2005068863 A1 WO2005068863 A1 WO 2005068863A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- constant velocity
- guide groove
- diameter
- pcd
- velocity joint
- 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
- F16D3/2237—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 where the grooves are composed of radii and adjoining straight lines, i.e. undercut free [UF] type joints
-
- 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
-
- 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
-
- 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
- F16D2003/22309—Details of grooves
-
- 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, for example, a constant velocity joint that connects one transmission shaft and the other transmission shaft in a driving force transmission unit of an automobile.
- Japanese Patent Application Laid-Open No. 2001-330051 discloses a fixed type including an outer joint member, an inner joint member, eight torque transmission balls, and a cage.
- JP 2003-97590 discloses a fixed constant velocity universal joint including an outer race, an inner race, six torque transmission balls and a cage, and the drive shaft diameter is d.
- the torque transmission ball diameter D and the pitch circle diameter of the six torque transmission balls are D.
- D Zd which is the ratio of the torque transmission pole diameter D to the drive shaft diameter d, is 0.6.
- D ZD is set to 3.4-3.8.
- ENGINEERING SERIES NO.7 (USA), 2nd edition, THE SOCIETYOF AUTOMOTIVE ENGINEERS.INC. 1991, p. 145—149 (hereinafter referred to as general literature) includes On the drive shaft), a zepper type constant velocity joint having an outer race ball groove center and an inner race ball groove center which are offset by equal distances on both sides of the joint center is disclosed.
- the general literature includes a common normal to the load side contact point between the ball race (guide groove) of the outer race and the ball, and the load side contact between the ball groove (guide groove) of the inner race and the ball. It describes that the wedge angle, which is the angle formed by the common normal of the points, is set to about 15 degrees to 17 degrees. This is to prevent the ball from locking due to friction when the Tsutsuba constant velocity joint performs a declination operation at a joint angle of around 0 degrees.
- a generally used ball groove cross section (a cross section in a direction perpendicular to the joint axis) is formed into an arc shape or an elliptic arc shape, and the ball in the elliptic arc shape ball groove
- the contact angle is set to 30 degrees to 45 degrees, and the most commonly used contact angle is described to be 45 degrees.
- Japanese Patent Application Laid-Open No. 2003-4062 and Japanese Patent Application Laid-Open No. 9-317784 include a water race, an inner race, eight balls, and a cage, and a groove of a guide groove (track groove) of the water race.
- the center of the curved part of the guide groove (track groove) of the inner race is the center of the outer diameter surface with respect to the center of the outer diameter surface.
- a fixed type constant velocity universal joint that is offset to the opposite side by an equal distance (F) in the axial direction is disclosed.
- Japanese Patent Application Laid-Open No. 2002-323061 discloses a fixed type constant velocity universal joint including an outer joint member, an inner joint member, eight torque transmission balls and a cage.
- the center of the ball groove (track groove) of the inner joint and the center of the ball groove (track groove) of the inner joint member are offset to the opposite side by an equal distance in the axial direction.
- the difference between the pitch circle diameter of the groove and the pitch circle diameter of the ball groove of the inner joint member is described as 5-50 m.
- the PCD clearance is set to 5 to 50 ⁇ m, so that a fixed type constant velocity universal joint having eight torque transmission balls can be used at a high load. It is said that it is possible to improve the durability and stability of the life variation.
- JP 2002-323061 A discloses that the radial gap between the outer joint member and the cage is 20 to 100 m, and the radial gap between the cage and the inner joint member. Is stated to be 20-100 ⁇ m!
- this type of constant velocity joint is, for example, as shown in FIG. 24, an outer member in which a plurality of curved guide grooves lb are formed in the axial direction on a spherical inner surface 1a.
- a ball rolling groove is integrally formed by the curved guiding groove lb of the outer member 1 and the curved guiding groove 2b of the inner member 2, and the ball rolling groove has a torque transmitting ball.
- 3 is arranged. The ball 3 is held by a holding window 4 a formed in a substantially ring-shaped retainer 4.
- the joint strength when the angle is given to the outer member 1 and the inner member 2 is determined by the strength of the retainer 4. Therefore, in order to improve the joint strength when adding an angle, it is necessary to improve the strength of the retainer 4 itself.
- the inner sphere diameter of the retainer 4 is reduced while the outer sphere diameter is increased to increase the thickness of the retainer 4 (hereinafter referred to as the first method).
- the method of increasing the cross-sectional area on the side receiving the jumping force (hereinafter referred to as the second method) with respect to the jumping force of the ball 3 generated when the angle is set, and the column part existing between the holding windows 4a
- a method of increasing the cross-sectional area of 4b (hereinafter referred to as the third method) is mentioned.
- the retainer 4 becomes heavy and the width dimension increases, and the ball 3 bites into the curved guide groove lb.
- the durability of the outer member 1 is lowered.
- the retainer 4 may be unable to be assembled into the outer member 1 because the retainer 4 becomes wider.
- the holding window 4a is provided with a corner radius portion 4c, and the ratio of the curvature radius R of the corner radius portion 4c to the diameter D of the ball 3 RZD
- a constant velocity universal joint in which 0.22 ⁇ RZD is disclosed.
- the ball track formed by the ball groove of the water race and the ball groove of the inner race is formed in a wedge shape that gradually spreads in the axial direction from the back side of the opening portion of the water race to the opening side. Is done. Accordingly, since the ball grooves on the water race side and the inner race side are offset by an equal distance from the joint center, both The depth of the ball groove is not uniform in the axial direction.
- the offset amount (F), the center of the guide groove of the outer race or the center of the guide groove of the inner race, and the center of the ball is set to a predetermined value.
- the ball diameter can be set small, or the constant velocity joint itself
- a PCD (pitch circle diameter) clearance with respect to the ball track formed by a pair of mutually opposing ball grooves of the outer joint member and the inner joint member is provided. How to set is important. This is because if the PCD clearance is too small, it is difficult to assemble the ball when inserting the ball into the ball track, and the ball's smooth rolling motion is hindered due to the increased restraining force on the ball. Power. On the other hand, if the PCD clearance is too large, hitting noise is generated between the cage window and the ball, and joint vibration increases.
- An object of the present invention is to provide a constant velocity joint capable of reducing the surface pressure against the guide groove due to contact with the ball and improving the durability.
- Another object of the present invention is to provide a constant velocity joint capable of improving durability by preventing occurrence of chipping or wear of the shoulder portion of the guide groove.
- Another object of the present invention is to provide a constant velocity joint having six balls.
- the optimal side of the holding window of the retainer for various clearances is optimally set for the counter side which is directly connected to the joint life.
- An object of the present invention is to provide a constant velocity joint capable of improving the durability by reducing the surface pressure between the guide groove and the ball and between the inner side guide groove and the ball.
- Still another object of the present invention is to provide a constant velocity joint capable of setting various dimensions corresponding to miniaturization while maintaining various characteristics such as strength, durability, and load capacity. Decide to provide.
- Still another object of the present invention is to provide a constant velocity joint that can ensure the strength of the retainer and improve the assembly workability.
- the cross section of the first guide groove of the outer member is formed in an arc shape so as to make one-point contact with the ball
- the cross section of the second guide groove of the inner ring is formed in an elliptical arc shape.
- the contact angle between the second guide groove and the ball is set in a range of 15 degrees to 20 degrees with respect to the vertical line (L).
- the assembling property of the ball into the hole of the outer member is deteriorated, and the smooth rolling operation of the ball is hindered, resulting in durability. This is because of deterioration.
- the PCD clearance exceeds 100 m, the contact ellipse between the ball and the first and second guide grooves protrudes from the shoulder at the groove end under high load, increasing the surface pressure and chipping the shoulder. This is a force that degrades durability.
- the spherical clearance formed by adding the difference from the sphere diameter [(sphere diameter in the water)-(retainer outer sphere diameter)] + [((retainer inner sphere diameter)-(inner outer sphere diameter)] Set within the range of 50—200 ⁇ m! /.
- the spherical clearance is less than 50 m, seizure may occur due to poor lubrication between the inner surface of the outer member and the outer surface of the retainer and between the outer surface of the inner ring and the inner surface of the retainer. It is. On the other hand, when the spherical clearance exceeds 200 m, a hitting sound is generated between the outer member and the inner ring and the retainer, which adversely affects the merchantability.
- the ratio ⁇ ( ⁇ ) between the ball diameter (N) and the offset amount T of the center of curvature (H, R) of the first and second guide grooves is represented by the relational expression (0 12 ⁇ V ⁇ 0.14) is set so as to satisfy the above conditions, and it is possible to suitably prevent the shoulders formed on the ends of the first and second guide grooves from running or chipping or wear. Thus, the durability of the constant velocity joint can be improved.
- the ratio (Db / Dp) of the diameter (Db) of the ball to the dimension (Dp) of the outer / inner PCD where the outer PCD and the inner PCD are the same is 0.2 ⁇ ( It is preferable to set it within the range of (Db / Dp) ⁇ 0.5. In this case, if the dimensional ratio (DbZDp) is less than 0.2, there is a problem that the diameter force S of the ball becomes too small and the durability is lowered. On the other hand, the dimensional ratio (DbZDp) is 0.5. If it exceeds, the ball becomes larger and the thickness of the outer member becomes relatively thin and the strength decreases.
- the ratio (DoZDp) of the outer diameter (Do) of the outer member to the dimension (Dp) of the outer 'inner PCD where the outer PCD and the inner PCD are the same is 1.4 ⁇ (Do / Dp) ⁇ l. 8 is preferable.
- the dimensional ratio (DoZDp) is less than 1.4. If this is the case, there is a problem that the thickness of the filter member becomes thin and the strength decreases. On the other hand, if the dimensional ratio (DoZDp) exceeds 1.8, the outer diameter of the filter member increases and the size is reduced. It cannot be made.
- the dimension (Dp) of the outer PCD in which the outer PCD and the inner PCD are the same, and the diameter (D) of the inner diameter portion of the inner selection formed on the inner wall surface of the hole of the inner ring, Ratio (DpZD) is set within the range of 1.9 ⁇ (Dp / D) ⁇ 2.2, and the ball diameter (Db) and the size of the counter inner PCD (Dp) Ratio (DbZDp) is set within the range of 0.2 ⁇ (Db / Dp) ⁇ 0.5, and the outer diameter (Do) of the outer member and the dimension of the outer 'inner PCD (Dp)
- the ratio (Do / Dp) to is preferably set within the range of 1.4 ⁇ (Do / Dp) ⁇ l.
- the holding window has an opening length (WL) in the circumferential direction of the retainer, and the opening length (WL) and the diameter (N) of the Bonore.
- the ratio (WLZ N) is preferably set within the range of 1.30 ⁇ WL / N ⁇ 1.42.
- the holding window has a corner with a radius of curvature R, and the ratio (RZN) of the radius of curvature (R) to the diameter of the ball (N) is in the range of 0.23 ⁇ R / N ⁇ 0.45. Is preferably set within the range.
- first guide groove and the second guide groove may be formed to have a curved shape portion and a straight shape portion (Sl, S2) along the longitudinal direction.
- the first guide groove and the second guide groove are preferably formed so as to have only a curved portion along the longitudinal direction.
- FIG. 1 is a longitudinal sectional view along the axial direction of a constant velocity joint according to an embodiment of the present invention.
- FIG. 2 is a partially enlarged longitudinal sectional view of the constant velocity joint shown in FIG.
- Fig. 3 is a partial cross-sectional view of the constant velocity joint shown in Fig. 1 as viewed from the axial direction (arrow X direction).
- FIG. 4 is a partially enlarged cross-sectional view orthogonal to the axial direction of the constant velocity joint shown in FIG.
- FIG. 5 is a partially enlarged longitudinal sectional view showing the depth of the first guide groove of the constant velocity joint in the present embodiment.
- FIG. 6 is a partially enlarged longitudinal sectional view showing the depth of the first guide groove of the constant velocity joint according to the comparative example.
- FIG. 7 is an explanatory view showing the relationship between the contact angle between the second guide groove and the ball and the durability.
- FIG. 8A is a longitudinal sectional view showing an outer PCD which is the pitch circle diameter of the first guide groove formed in the outer cup
- FIG. 8B is a pitch circle diameter of the second guide groove formed in the inner ring. It is a longitudinal cross-sectional view which shows a certain inner PCD.
- Fig. 9A is a longitudinal sectional view showing the inner spherical diameter of the inner diameter surface of the outer cup
- Fig. 9B is a longitudinal sectional view showing the inner outer spherical diameter of the inner surface of the inner ring
- Fig. 9C is an outer surface of the retainer. It is a longitudinal section which shows a retainer outer sphere diameter and a retainer inner sphere diameter of an inner surface of a retainer, respectively.
- FIG. 10 is a longitudinal sectional view showing an offset amount between the window width center of the retaining window of the retainer and the spherical centers of the outer surface and the inner surface of the retainer.
- FIG. 11 is an explanatory diagram showing the relationship between PCD clearance and durability.
- FIG. 12 is an explanatory diagram showing the relationship between spherical clearance and durability.
- FIG. 13 is an explanatory diagram showing the relationship between window offset and durability.
- FIG. 14 is a partial cross-sectional side view of the constant velocity joint shown in FIG. 1 as viewed from the axial direction (arrow X direction).
- Fig.15 is a partially enlarged cross section of a constant velocity joint showing shaft selection diameter (D), water inner PCD (Dp), water force outer diameter (Do), ball diameter (Db), etc.
- D shaft selection diameter
- Dp water inner PCD
- Do water force outer diameter
- Db ball diameter
- FIG. 16 is a characteristic diagram showing a characteristic line L related to the relationship between the diameter of the inner diameter portion of the inner selection and the counter'inner PCD.
- FIG. 17 is a characteristic diagram showing a characteristic line M relating to the relationship between the outer “inner PCD” and the outer diameter of the outer cup.
- FIG. 18 is a characteristic diagram showing a characteristic line N relating to the relationship between the outer “inner PCD” and the inner width of the inner ring.
- FIG. 19 is a characteristic diagram showing a characteristic line Q relating to the relationship between the outer “inner PCD” and the ball diameter.
- FIG. 20 is a longitudinal sectional view along the axial direction of a constant velocity joint used for explaining the relationship between a holding window formed on a retainer and a ball.
- FIG. 21 is an exploded perspective view of the retainer and the balls constituting the constant velocity joint shown in FIG.
- FIG. 22 is a side view illustrating the dimensions of the retainer and the ball shown in FIG. 21 as seen from the circumferential direction.
- FIG. 23 is a longitudinal sectional view along the axial direction of a constant velocity joint used for explaining the first guide groove and the second internal groove having only a curved portion along the longitudinal direction.
- FIG. 24 is an exploded perspective view of a constant velocity joint according to the prior art.
- reference numeral 10 indicates a constant velocity joint according to an embodiment of the present invention.
- the vertical cross section refers to a cross section along the axial direction of the first shaft 12 and the second shaft 18, and the horizontal cross section refers to a cross section orthogonal to the axial direction.
- the constant velocity joint 10 is integrally connected to one end of the first shaft 12 and has a bottomed cylindrical cup (outer member) 16 having an opening 14 and one end of the second shaft 18.
- the inner member 22 is basically composed of an inner member 22 that is fixed to the inner portion of the outer cup 16 and accommodated in the hole of the outer cup 16.
- the inner wall of the outer cup 16 has an inner diameter surface that also has a spherical force.
- the first inner surface 24 has six first guide grooves 26a-26f extending along the axial direction and spaced by 60 degrees around the axis.
- the point H corresponds to the center of the outer cup 16 along the axial direction from the spherical center K of the inner diameter surface 24 (the intersection where the imaginary plane (ball central plane) connecting the central point O of the ball 28 and the joint shaft 27 intersects). It is placed at a position offset by a distance T1 on the opening 14 side.
- the cross sections of the first guide grooves 26a to 26f formed in the outer cup 16 each have a single center of curvature A on a vertical line L passing through the center O of the ball 28 as shown in FIG.
- the first guide grooves 26a to 26f are formed so as to be in contact with an outer surface of a ball 28, which will be described later, at one point B on the drawing.
- the inner diameter surface 24 is continuously formed on both sides of the first guide groove 26a-26f in the transverse section, and a boundary portion between the first guide groove 26a-26f, the end portion, and the inner diameter surface 24 is formed.
- a pair of chamfered first shoulder portions 30a and 30b are formed.
- the contact angle of the ball 28 with respect to the first guide grooves 26a to 26f of the outer cup 16 is set to zero degree with respect to the lead straight line L. Further, the ratio (MZN) of the groove radius M and the diameter N of the ball 28 in the transverse plane of the first guide grooves 26a to 26f may be set to 0.51-0.55 (see FIG. 4).
- the inner member 22 includes an inner ring 34 formed with a plurality of second guide grooves 32a to 32f corresponding to the first guide grooves 26a to 26f along the circumferential direction of the outer peripheral surface,
- the first guide groove 26a-26f formed on the wall surface and the second guide groove 32a-32f formed on the outer diameter surface 35 (see FIG. 4) of the inner ring 34 are arranged to be able to roll.
- a plurality of (in this embodiment, six) balls 28 that perform a rotational torque transmission function and a plurality of holding windows 36 that hold the balls 28 are formed along the circumferential direction, and the outer cup 16 and the inner ring 3 are formed. 4 and a retainer 38 interposed therebetween.
- the inner ring 34 is spline-fitted to the end of the second shaft 18 through a hole formed at the center, or is attached to the annular groove of the second shaft 18. It is integrally fixed to the end portion of the second shaft 18 via the member 40.
- the second guide grooves 32a to 32f formed in the inner ring 34 and having a longitudinal section along the axial direction formed in a curved shape have a point R as the center of curvature, as shown in FIG.
- the point R corresponds to the spherical center K of the inner diameter surface 24 (the virtual plane connecting the center point O of the ball 28 (ball It is arranged at a position offset by a distance T2 along the axial direction from the intersection of the center plane) and the joint shaft 27 at right angles.
- the point ⁇ is located on the opening 14 side of the outer cup 16 with respect to the spherical center ⁇ , and the point R is located on the back 46 side of the outer cup 16, and the radius of curvature of the point ⁇ ⁇ and the curvature of the point R are The radius is set so that it crosses like a cross (see Figure 2).
- the diameter of the ball 28 is ⁇
- the offset amount of the center of curvature (point H, point R) of the first guide groove 26a-26f of the outer cup 16 and the second guide groove 32a-32f of the inner ring 34 is T
- the diameter N and the offset amount T of the ball 28 are set so as to satisfy the relational expression ⁇ 0.14.
- the second guide groove 32a-32f has a cross section having an elliptical arc shape having a pair of centers C and D spaced apart by a predetermined distance along the horizontal direction.
- the inner grooves 32a to 32f are formed so as to contact the outer surface of the ball 28 at two points E and F in the drawing.
- the outer surface of the ball 28 and the second guide grooves 32a-32f are formed so as to make a surface contact rather than a point contact.
- the outer diameter surface 35 is continuously formed on both sides of the second guide groove 32a-32f in the transverse section, and a boundary portion between the second guide groove 32a- 32f and the end and the outer diameter surface 35 is formed.
- a pair of chamfered second shoulder portions 42a and 42b are formed on the surface.
- the contact angle oc of the ball 28 with respect to the second guide grooves 32a-32f is set so as to be separated by an equal angle ⁇ from the vertical line L to the left and right.
- the contact angle ⁇ of the ball 28 with respect to the second guide groove 32a-3 2f is set within a range of 13 degrees to 22 degrees as shown in FIG. 7, the durability is improved.
- the contact angle oc of the ball 28 to the guide groove 32a-32f is set within a range of 15 degrees to 20 degrees, extremely good durability can be obtained.
- the groove radii P and Q in the cross section of the second guide groove 32a-32f and the ball 28 The ratio to the diameter N (PZN, QZN) should be set to 0.51-0.55 (see Figure 4).
- the balls 28 are formed of, for example, steel balls, and each of the balls 28 extends in the circumferential direction between the first guide grooves 26a-26f of the outer cup 16 and the second guide grooves 32a-32f of the inner ring 34. It is arranged so that it can roll individually.
- the ball 28 transmits the rotational torque of the second shaft 18 to the first shaft 12 through the inner ring 34 and the outer cup 16, and along the first guide grooves 26a and 26f and the second guide grooves 32a to 32f.
- the rotational torque is suitably transmitted from either direction between the first shaft 12 and the second shaft 18.
- the PCA is the PCD
- the pitch circle diameter of the second guide grooves 32a-32f is the inner PC D when the six balls 28 are in point contact with the second guide grooves 32a-32f of the inner ring 34, respectively.
- the PCD clearance is set based on the difference between the counter PCD and the inner PCD (outer PCD inner PCD).
- the difference between the inner spherical surface diameter of the outer cup 24 at the inner diameter surface 24 of the outer cup 16 and the outer spherical surface diameter of the retainer 38 and the inner diameter surface of the retainer 38 The spherical clearance is set by adding the difference between the inner spherical diameter of the retainer and the outer outer spherical diameter of the inner ring 34.
- spherical clearance [(inner sphere diameter) (retainer outer sphere diameter)] + [(retainer inner sphere diameter) (inner outer sphere diameter)].
- the window width center of the holding window 36 of the retainer 38 (the axial direction of the retainer 38 is the width) and the spherical centers of the outer surface 38a and the inner surface 38b of the retainer 38 are It is arranged at a position offset by a predetermined distance along the axial direction of the retainer 38.
- the constant velocity joint 10 is basically configured as described above. Next, the operation and action and effects thereof will be described.
- the six balls 28 held by the holding window 36 of the retainer 38 are positioned on the constant velocity surface or the bisector angle plane between the first shaft and the second shaft 12, 18, so that The driving contact is always maintained on the constant velocity surface, ensuring constant velocity.
- the angular displacement of the first shaft 12 and the second shaft 18 is preferably allowed while maintaining the constant velocity.
- the diameter N of the ball 28 and the center of curvature of the first guide grooves 26a-26f of the outer cup 16 and the second guide grooves 32a-32f of the inner ring 34 (point H, point offset amount (
- the wedge angle formed by the first guide grooves 26a-26f and the second guide grooves 32a-32f when the ratio V of the diameter N of the ball 28 to the offset amount T is less than 0.12. Is in a minimum state, and the ball 28 is easily locked during non-rotating operation, resulting in poor workability during assembly.
- the ratio V between the diameter N of the ball 28 and the offset amount T exceeds 0.14, the depths of the first and second guide grooves 26a-26f, 32a-32f will become shallow, The first and second guide grooves 26a-26f, 32a-32f can prevent the first and second shoulder portions 30a, 30b, 42a, 42b from getting on or chipping or wearing. It becomes difficult.
- the diameter N of the ball 28 and the offset amount T of the center of curvature (point H, point R) of the first and second guide grooves 26a-26f, 32a-32f are expressed by the above relational expression (0.12).
- ⁇ V ⁇ 0.14) is set to satisfy the first and second shoulders 30a, 30b formed at the ends of the first and second guide grooves 26a-26f, 32a-32f,
- the durability of the constant velocity joint 10 can be further improved by suitably preventing the occurrence of chipping or chipping or wear of 42a and 42b.
- FIG. 5 shows a partial enlargement in the longitudinal section of the constant velocity joint 10 according to the present embodiment.
- the diameter N of the ball 28 and the curvature centers of the first and second guide grooves 26a-26f, 32a-32f By satisfying the above relational expression with respect to the relationship between the point H and the offset amount of the point, the offset The volume Tl is set small.
- FIG. 6 shows a partial enlargement in the longitudinal section of the constant velocity joint 100 according to the comparative example, and the offset amount T2 is set larger than that in the present embodiment (T1 ⁇ T2).
- the depth of the first guide grooves 26a-26f of the outer cup 16 when comparing the depth of the first guide grooves 26a-26f of the outer cup 16 at a portion inclined by about 15 degrees with respect to the straight line S perpendicular to the joint shaft 27 and passing through the center of the ball 28, Since the depth DPI of the first guide groove 26a-26f of the embodiment can be formed larger than the depth DP2 of the first guide groove of the comparative example (DPI> DP2), the first guide groove 26a-26f
- the first and second shoulder portions 30a, 30b, 42a, 42b formed at the end portions of the first and second shoulder portions 30a, 42b, 42b can be suitably prevented from getting on or being chipped or worn.
- the cross section of the first guide grooves 26a to 26f of the outer cup 16 is formed in an arc shape so as to make one-point contact with the ball 28, and the second guide of the inner ring 34
- the cross section of the groove 32a-32f into an elliptical arc shape and making contact with the ball 28 at two points, the first guide grooves 26a-26f and second Durability can be improved by reducing the surface pressure against the guide grooves 32a-32f.
- the ratio of the groove radius (M, P, Q) and the diameter N of the ball 28 in the cross section of the first guide groove 26a-26f and the second guide groove 32a-32f are set in the range of 0.51-0.55, respectively, and the contact angle of the first guide grooves 26a-26f with the ball 28 is set to zero degrees with respect to the vertical line L, Furthermore, by setting the contact angle a between the second guide groove 32a-32f and the ball 28 within the range of 13 degrees to 22 degrees with respect to the vertical line L, the surface pressure can be reduced and the durability can be further improved. Can do.
- the ratio of the groove radius (M, P, Q) to the diameter N of the ball 28 in the cross section of the first guide groove 26a-26f and the second guide groove 32a-32f is 0.51-0.55.
- the reason for this is that if the radius is less than 0.51, the groove radius (M, P, Q) and the diameter N of the ball 28 are too close to each other, so that it is close to a solid contact (full contact) and the ball 28 rolls. This is because the durability deteriorates due to the deterioration of the contact resistance. On the other hand, if it exceeds 0.55, the contact ellipse of the ball 28 becomes smaller, and the contact surface pressure increases and the durability deteriorates.
- the reason why the contact angle oc of the ball 28 with respect to the second guide grooves 32a-32f is set in the range of 13 degrees to 22 degrees is that if the contact angle ex is less than 13 degrees, the load on the ball 28 is When the contact angle ⁇ exceeds 22 °, the end of the second guide grooves 32a-32f (second shoulders 42a, 42b) and the ball 28 This is because the contact positions of the contact ellipse are close to each other, and the contact ellipse protrudes and the surface pressure increases, so that the durability deteriorates.
- the PCD clearance (see FIGS. 8A and 8B) formed by the difference between the counter PCD and the inner PCD (the counter PCD inner PCD) is preferably 0-100 m, Should be set to 0 – 60 m.
- the reason why the PCD clearance is set to 0-100 m is that if it is less than 0 ⁇ m, the assembly of the ball 28 is deteriorated and the smooth rolling operation of the ball 28 is hindered and the durability is deteriorated. It is.
- the first and second shoulder portions 30a whose contact ellipses between the ball 28 and the first and second guide grooves 26a-26f, 32a-32f are groove ends when the load is high.
- the contact pressure increases, and the first and second shoulder portions 30a, 30b, 42a, and 42b are chipped and the durability deteriorates.
- extremely good durability can be obtained by setting the PCD setting range to 0-60 m.
- the spherical clearance set by (diameter)] should be 50-200 m, preferably 50-150 m! / ⁇ . If it is less than 50 / zm, seizure may occur due to poor lubrication between the inner surface of the water cup 16 and the outer surface 38a of the retainer 38, and between the outer surface of the inner ring 34 and the inner surface 38b of the retainer 38, and may have a negative effect. .
- the window width center of the holding window 36 of the retainer 38 (the axial direction of the retainer 38 is the width) 1S
- the outer surface 38a and the inner surface 38b of the retainer 38 It is arranged at a position offset by 20-100 ⁇ m along the axial direction of the retainer 38 from the center of the spherical surface. If the offset amount between the window width center of the retainer 38 and the center of the spherical surface is smaller than 20 ⁇ m, it will be difficult to ensure constant speed due to insufficient restraint force of the ball 28, and if it exceeds 100 m, the restraint force will be excessive. This is because the smooth rolling motion of the ball 28 is hindered and the durability deteriorates. In this case, as shown in the experimental results of FIG. 13, by setting the offset amount setting range between the window width center and the spherical center of the retainer 38 to 40 to 80 ⁇ m, extremely good durability can be obtained. can get.
- the diameter (D) of the inner selection inner diameter portion 39 is arbitrarily set, and based on the diameter (D) of the inner selection inner diameter portion 39, the inner wall 34 is the minimum wall thickness of the inner ring 34. Set the dimension of D (see Figure 14 and Figure 15).
- the diameter (D) of the inner selection inner diameter portion 39 passes through the center of the hole of the inner ring 34, and the bottom of the valley portion of one inner selection inner diameter portion 39 and the other inner selection inner diameter 39. This is the dimension (maximum diameter) between the bottom of the valley part of part 39 (see Fig. 15).
- the minimum thickness of the inner ring 34 ensures a predetermined bond strength.
- the value of the counter's inner PCD is obtained from a characteristic straight line L relating to the relationship between the diameter of the inner selection inner diameter portion 39 and the counter's inner PCD, as shown in FIG. In this case, when the diameter of the inner selection inner diameter portion 39 is D and the outer inner PCD is Dp (see FIG. 14 and FIG. 15), the outer inner PCD (Dp) and the inner selection inner diameter
- the size ratio (DpZD) of the portion 39 to the diameter (D) is preferably set within a range of 1.9 ⁇ (Dp / D) ⁇ 2.2.
- the outer diameter of the outer cup 16 is set based on a characteristic line M relating to the relationship between the outer diameter of the cup portion of the outer cup 16 and the outer “inner PC D”.
- the dimensional ratio (Do / Dp) between the outer diameter (Do) of the outer cup 16 and the outer inner PCD (Dp). Is preferably set within the range of 1.4 ⁇ (Do / Dp) ⁇ 1.8.
- the inner ring 3 Set the ring width of 4.
- the dimensional ratio (W / Dp) between the ring width (W) of the inner ring 34 and the water inner PCD (Dp) is 0.38 ⁇ (W / Dp ) ⁇ 0.42 is preferable.
- the diameter of the ball 28 is set based on the characteristic straight line Q relating to the relationship between the diameter of the ball 28 and the outer “inner PCD”.
- the dimension ratio (DbZDp) of the diameter (Db) of the ball 28 and the outer PCD (Dp) is 0.2 ⁇ It is preferable to set it within the range of (Db / Dp) ⁇ 0.5.
- the dimensional ratio (DbZDp) is less than 0.2, there is a problem that the diameter of the ball 28 becomes too small and durability is lowered. On the other hand, the dimensional ratio (DbZDp) is less than 0.5. If the ball 28 becomes larger and the thickness of the outer cup 16 becomes relatively thin, the strength decreases. There is a problem.
- the inner sphere diameter and the outer sphere diameter of the retainer 38 that holds the ball 28 are arbitrarily set according to the layout.
- the inner surface 24 of the water cup 16 extends along the axial direction (arrow X direction), and has six first holes spaced about 60 degrees around the axis.
- 1 guide groove 26a-2 6f is formed, and each of the first guide grooves 26a-26f has a linear shape portion S1 provided integrally from the curved shape portion along the longitudinal direction (arrow X direction).
- each of the second guide grooves 32a to 32f has a linear shape portion S2 provided integrally from the curved shape portion along the longitudinal direction (arrow X direction), and each of the linear shape portions Sl and S2 is an arrow. They are placed in opposite directions along the X direction.
- the retainer 38 has a substantially ring shape, and six holding windows 36 each holding the ball 28 are formed at equal angular intervals along the circumferential direction.
- each holding window 36 has an opening length (WL) in the circumferential direction of the retainer 38, and the opening length (WL) and the diameter (N) of the ball 28.
- the ratio WLZN is set to 1. 30 ⁇ WL / N ⁇ l.42.
- Each holding window 36 has a corner 36a with a radius of curvature R, and the ratio RZN between the radius of curvature R and the diameter (N) of the ball 28 is a relationship of 0.23 ⁇ R / N ⁇ 0.45.
- the retainer 38 in each holding window 36 of the retainer 38, the circumferential opening length (WL) of the retainer 38, the diameter (N) of the ball 28, and the force WL The relationship is set to /N ⁇ 1.42. For this reason, the retainer 38 can effectively maintain the circumferential length of the column portion 136 between the holding windows 36, and the cross-sectional area of the column portion 136 can be reduced without having to increase the thickness of the retainer 38. It becomes possible to improve. Accordingly, the retainer 38 has, for example, a strength of the retainer 38 that prevents the inner sphere diameter dimension from being set small and the outer sphere diameter dimension from being set large or the axial width dimension from becoming long. The effect that it can improve favorably is acquired.
- the constant velocity joint 10 In the constant velocity joint 10, the relationship between the opening length (WL) of the holding window 36, the diameter (N) of the ball 28, and the force 1.30 ⁇ WLZN is set. As a result, it is possible to increase the opening area of each holding window 36, and to effectively prevent a defective assembly of the ball 28, a defective assembly of the inner ring 34, and the like. For this reason, the constant velocity joint 10 has an advantage that the assembly workability can be easily improved with a simple configuration.
- the maximum principal stress load of the column portion 136 between the holding windows 36 can be reduced, and the strength of the retainer 38 can be improved.
- the first guide grooves 26a-26f have the straight-shaped portion S1 along the longitudinal direction
- the second guide grooves 32a-32f have the linear-shaped portion along the longitudinal direction.
- the first guide grooves 26a-26f and the second guide grooves 32a-32 may be formed so as to have only curved portions along the longitudinal direction.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Rolling Contact Bearings (AREA)
- Forging (AREA)
- Pivots And Pivotal Connections (AREA)
Abstract
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE602005025450T DE602005025450D1 (de) | 2004-01-15 | 2005-01-13 | Homokinetisches gelenk |
EP05703556A EP1707835B1 (en) | 2004-01-15 | 2005-01-13 | Constant velocity joint |
US10/586,185 US7632190B2 (en) | 2004-01-15 | 2005-01-13 | Constant velocity joint |
Applications Claiming Priority (12)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2004008524A JP4681235B2 (ja) | 2004-01-15 | 2004-01-15 | 等速ジョイント |
JP2004-008524 | 2004-01-15 | ||
JP2004194230A JP4217195B2 (ja) | 2004-06-30 | 2004-06-30 | 等速ジョイント |
JP2004-194274 | 2004-06-30 | ||
JP2004194274A JP4268572B2 (ja) | 2004-06-30 | 2004-06-30 | 等速ジョイント |
JP2004-192637 | 2004-06-30 | ||
JP2004-194230 | 2004-06-30 | ||
JP2004192637A JP2006017143A (ja) | 2004-06-30 | 2004-06-30 | 等速ジョイント |
JP2004358176A JP2006162023A (ja) | 2004-12-10 | 2004-12-10 | 等速ジョイント |
JP2004-358176 | 2004-12-10 | ||
JP2005-003787 | 2005-01-11 | ||
JP2005003787A JP4880902B2 (ja) | 2005-01-11 | 2005-01-11 | 等速ジョイント |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2005068863A1 true WO2005068863A1 (ja) | 2005-07-28 |
Family
ID=34799924
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2005/000317 WO2005068863A1 (ja) | 2004-01-15 | 2005-01-13 | 等速ジョイント |
Country Status (4)
Country | Link |
---|---|
US (1) | US7632190B2 (ja) |
EP (3) | EP1707835B1 (ja) |
DE (1) | DE602005025450D1 (ja) |
WO (1) | WO2005068863A1 (ja) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2007036237A1 (de) * | 2005-09-23 | 2007-04-05 | Gkn Driveline International Gmbh | Optimiertes gleichlauffestgelenk mit hinterschnittfreien kugelbahnen |
US8292749B2 (en) | 2007-09-26 | 2012-10-23 | Ntn Corporation | Fixed type constant velocity universal joint |
WO2019026596A1 (ja) * | 2017-08-02 | 2019-02-07 | Thk株式会社 | スプライン構造、減速又は増速装置、等速ジョイント |
Families Citing this family (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP2149719B1 (en) * | 2007-03-27 | 2013-06-19 | NTN Corporation | Fixed uniform-motion universal coupling |
DE102007059379B4 (de) * | 2007-12-10 | 2016-12-15 | Volkswagen Ag | Kugelverschiebegelenk |
US8323116B2 (en) * | 2007-12-17 | 2012-12-04 | Steering Solutions Ip Holding Corporation | Universal joint |
US8235829B2 (en) * | 2009-03-02 | 2012-08-07 | Steering Solutions Ip Holding Corporation | Constant velocity joint |
DE102010009685B4 (de) * | 2009-03-02 | 2017-10-19 | GM Global Technology Operations LLC (n. d. Gesetzen des Staates Delaware) | Gleichlaufgelenk |
BRPI1001172A2 (pt) | 2009-03-13 | 2015-08-18 | Gm Global Tech Operations Inc | Junta de velocidade constante e método de fabricar uma junta de velocidade constante |
DE102010013006A1 (de) * | 2009-03-27 | 2011-04-28 | GM Global Technology Operations, Inc., Detroit | Gleichlaufgelenk |
US8444495B2 (en) * | 2009-10-20 | 2013-05-21 | Hyundai Wia Corporation | Cross groove type constant velocity joint |
JP5340897B2 (ja) * | 2009-11-25 | 2013-11-13 | Ntn株式会社 | 固定式等速自在継手 |
JP5964030B2 (ja) * | 2011-11-11 | 2016-08-03 | Ntn株式会社 | 固定式等速自在継手 |
CN112434389A (zh) * | 2020-11-23 | 2021-03-02 | 上海纳铁福传动系统有限公司 | 汽车传动轴、变直径轴管及其弯曲振动频率优化方法 |
Citations (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH09317783A (ja) * | 1996-05-28 | 1997-12-09 | Ntn Corp | 自動車用固定型等速自在継手 |
JPH11218147A (ja) * | 1998-01-30 | 1999-08-10 | Nippon Seiko Kk | 等速ジョイント |
JP2000018267A (ja) * | 1998-06-26 | 2000-01-18 | Nippon Seiko Kk | 等速ジョイント |
JP2000266071A (ja) * | 1999-03-12 | 2000-09-26 | Ntn Corp | 等速自在継手 |
FR2797924A1 (fr) | 1999-08-30 | 2001-03-02 | Gkn Automotive Ag | Joint homocinetique a billes avec des pistes dont la deuxieme derivee partant du fond de piste est constamment croissante |
JP2002013544A (ja) * | 2000-06-27 | 2002-01-18 | Ntn Corp | 等速自在継手 |
JP2002323061A (ja) * | 2001-04-24 | 2002-11-08 | Ntn Corp | 等速自在継手 |
JP2002372067A (ja) * | 2001-06-18 | 2002-12-26 | Ntn Corp | プロペラシャフト用等速自在継手 |
JP2003042146A (ja) * | 2001-01-30 | 2003-02-13 | Nsk Ltd | コンプレッサ用プーリの回転支持装置 |
JP2003097590A (ja) * | 2001-09-21 | 2003-04-03 | Toyoda Mach Works Ltd | 等速ジョイント |
JP2003307235A (ja) * | 1996-05-28 | 2003-10-31 | Ntn Corp | 等速自在継手 |
Family Cites Families (24)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3076323A (en) * | 1961-03-14 | 1963-02-05 | Loehr & Bromkamp Gmbh | Pivot joint assembly |
JPH06109028A (ja) | 1992-09-30 | 1994-04-19 | Ntn Corp | 等速自在継手 |
DE69636726T2 (de) * | 1995-12-26 | 2008-02-21 | Ntn Corp. | Gleichlaufgelenke |
JP3859267B2 (ja) | 1996-05-28 | 2006-12-20 | Ntn株式会社 | 固定型等速自在継手 |
EP1326027B1 (en) | 1997-07-16 | 2006-02-01 | Nsk Ltd | Constant velocity joint for wheels |
GB2331570B (en) | 1997-11-19 | 2002-06-05 | Gkn Hardy Spicer Ltd | Torque-transmitting devices |
DE19808029C1 (de) | 1998-02-26 | 1999-12-30 | Gkn Automotive Ag | Kugelgleichlaufdrehgelenk |
US6299542B1 (en) * | 1998-04-15 | 2001-10-09 | Nsk Ltd. | Constant velocity joint and rolling bearing unit for wheel |
JP4067191B2 (ja) | 1998-08-10 | 2008-03-26 | 日本精工株式会社 | 等速ジョイント及び等速ジョイント付転がり軸受ユニット |
JP2000145805A (ja) | 1998-11-11 | 2000-05-26 | Nsk Ltd | 等速ジョイント及び等速ジョイント付自動車用ハブユニット |
JP2000240673A (ja) * | 1999-02-23 | 2000-09-05 | Ntn Corp | プロペラシャフト用等速自在継手、及びプロペラシャフト |
EP1079128B1 (en) * | 1999-03-12 | 2006-05-24 | Ntn Corporation | Constant velocity universal joint |
JP4219472B2 (ja) | 1999-03-12 | 2009-02-04 | Ntn株式会社 | 等速自在継手 |
US6431988B1 (en) * | 1999-09-17 | 2002-08-13 | Ntn Corporation | Fixed type constant velocity joint and assembling method therefor |
JP4262863B2 (ja) | 2000-06-02 | 2009-05-13 | Ntn株式会社 | 固定型等速自在継手 |
FR2799519A1 (fr) * | 1999-10-08 | 2001-04-13 | Pierre Guimbretiere | Joint homocinetique fixe a billes |
JP2001171308A (ja) * | 1999-12-15 | 2001-06-26 | Ntn Corp | 駆動車輪用軸受装置 |
JP2001330051A (ja) | 2000-05-19 | 2001-11-30 | Ntn Corp | 等速自在継手 |
US6506122B2 (en) * | 2000-05-19 | 2003-01-14 | Ntn Corporation | Constant velocity universal joint |
JP4459388B2 (ja) | 2000-06-07 | 2010-04-28 | Ntn株式会社 | 自動車用プロペラシャフト |
JP2003004062A (ja) | 2001-06-25 | 2003-01-08 | Ntn Corp | 固定型等速自在継手 |
US20030017877A1 (en) * | 2001-04-24 | 2003-01-23 | Masazumi Kobayashi | Constant velocity universal joint |
US6913540B2 (en) | 2001-05-10 | 2005-07-05 | Ntn Corporation | Constant velocity universal joint for propeller shaft |
US20030054893A1 (en) * | 2001-09-20 | 2003-03-20 | Delphi Technologies Inc. | Constant velocity joint |
-
2005
- 2005-01-13 EP EP05703556A patent/EP1707835B1/en not_active Expired - Fee Related
- 2005-01-13 DE DE602005025450T patent/DE602005025450D1/de active Active
- 2005-01-13 EP EP10005254A patent/EP2233764A3/en not_active Withdrawn
- 2005-01-13 US US10/586,185 patent/US7632190B2/en not_active Expired - Fee Related
- 2005-01-13 EP EP10005253A patent/EP2228557A1/en not_active Withdrawn
- 2005-01-13 WO PCT/JP2005/000317 patent/WO2005068863A1/ja active Application Filing
Patent Citations (12)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH09317783A (ja) * | 1996-05-28 | 1997-12-09 | Ntn Corp | 自動車用固定型等速自在継手 |
JP2003307235A (ja) * | 1996-05-28 | 2003-10-31 | Ntn Corp | 等速自在継手 |
JPH11218147A (ja) * | 1998-01-30 | 1999-08-10 | Nippon Seiko Kk | 等速ジョイント |
JP2000018267A (ja) * | 1998-06-26 | 2000-01-18 | Nippon Seiko Kk | 等速ジョイント |
JP2000266071A (ja) * | 1999-03-12 | 2000-09-26 | Ntn Corp | 等速自在継手 |
FR2797924A1 (fr) | 1999-08-30 | 2001-03-02 | Gkn Automotive Ag | Joint homocinetique a billes avec des pistes dont la deuxieme derivee partant du fond de piste est constamment croissante |
JP2003508697A (ja) * | 1999-08-30 | 2003-03-04 | ジー・ケー・エヌ・オートモーティヴ・ゲゼルシャフト・ミット・ベシュレンクテル・ハフツング | 定速度自在ボール継ぎ手 |
JP2002013544A (ja) * | 2000-06-27 | 2002-01-18 | Ntn Corp | 等速自在継手 |
JP2003042146A (ja) * | 2001-01-30 | 2003-02-13 | Nsk Ltd | コンプレッサ用プーリの回転支持装置 |
JP2002323061A (ja) * | 2001-04-24 | 2002-11-08 | Ntn Corp | 等速自在継手 |
JP2002372067A (ja) * | 2001-06-18 | 2002-12-26 | Ntn Corp | プロペラシャフト用等速自在継手 |
JP2003097590A (ja) * | 2001-09-21 | 2003-04-03 | Toyoda Mach Works Ltd | 等速ジョイント |
Non-Patent Citations (1)
Title |
---|
See also references of EP1707835A4 * |
Cited By (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2007036237A1 (de) * | 2005-09-23 | 2007-04-05 | Gkn Driveline International Gmbh | Optimiertes gleichlauffestgelenk mit hinterschnittfreien kugelbahnen |
JP2009509106A (ja) * | 2005-09-23 | 2009-03-05 | ジーケイエヌ ドライヴライン インターナショナル ゲゼルシャフト ミット ベシュレンクテル ハフツング | アンダーカットレス球軌道を備えた等速形自在軸継手 |
US8292749B2 (en) | 2007-09-26 | 2012-10-23 | Ntn Corporation | Fixed type constant velocity universal joint |
WO2019026596A1 (ja) * | 2017-08-02 | 2019-02-07 | Thk株式会社 | スプライン構造、減速又は増速装置、等速ジョイント |
TWI761565B (zh) * | 2017-08-02 | 2022-04-21 | 日商Thk股份有限公司 | 減速或增速裝置 |
US11493092B2 (en) | 2017-08-02 | 2022-11-08 | Thk Co., Ltd. | Speed-reducing or -increasing apparatus |
Also Published As
Publication number | Publication date |
---|---|
EP2233764A3 (en) | 2010-12-08 |
EP1707835A1 (en) | 2006-10-04 |
US7632190B2 (en) | 2009-12-15 |
EP2228557A1 (en) | 2010-09-15 |
EP2233764A2 (en) | 2010-09-29 |
DE602005025450D1 (de) | 2011-02-03 |
US20070161428A1 (en) | 2007-07-12 |
EP1707835B1 (en) | 2010-12-22 |
EP1707835A4 (en) | 2009-09-09 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
WO2005068863A1 (ja) | 等速ジョイント | |
CN100476227C (zh) | 等速万向节 | |
JP4880902B2 (ja) | 等速ジョイント | |
EP0950824A2 (en) | Constant velocity joint and rolling bearing unit for wheel | |
US7758430B2 (en) | Structure for tripod constant velocity joint and method of assembling roller assembly | |
JPH1073129A (ja) | 摺動型等速自在継手 | |
CN101268294B (zh) | 滑动式等速万向接头 | |
JP4994689B2 (ja) | 固定式等速自在継手 | |
JP2007270997A (ja) | 固定式等速自在継手 | |
KR20090094400A (ko) | 케이지 오프셋을 갖는 조인트 배열 | |
WO2006100893A1 (ja) | クロスグルーブ型等速自在継手 | |
JP2006266329A (ja) | 固定型等速自在継手 | |
US8282495B2 (en) | Fixed type constant velocity universal joint | |
JP2003021159A (ja) | 等速自在継手 | |
US20050202881A1 (en) | Constant velocity joint | |
JP3767168B2 (ja) | 等速ジョイント及び等速ジョイント付車輪用転がり軸受ユニット | |
JP4268572B2 (ja) | 等速ジョイント | |
JP2007024106A (ja) | 固定型等速自在継手 | |
JP4217195B2 (ja) | 等速ジョイント | |
JP2007170422A (ja) | 固定式等速自在継手 | |
JP4896673B2 (ja) | 固定式等速自在継手及びその製造方法 | |
JP2007016899A (ja) | 固定型等速自在継手 | |
WO2018123394A1 (ja) | 固定式等速自在継手 | |
JP2008261404A (ja) | 固定式等速自在継手 | |
JP2006162023A (ja) | 等速ジョイント |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
AK | Designated states |
Kind code of ref document: A1 Designated state(s): AE AG AL AM AT AU AZ BA BB BG BR BW BY BZ CA CH CN CO CR CU CZ DE DK DM DZ EC EE EG ES FI GB GD GE GH GM HR HU ID IL IN IS KE KG KP KR KZ LC LK LR LS LT LU LV MA MD MG MK MN MW MX MZ NA NI NO NZ OM PG PH PL PT RO RU SC SD SE SG SK SL SY TJ TM TN TR TT TZ UA UG US UZ VC VN YU ZA ZM ZW |
|
AL | Designated countries for regional patents |
Kind code of ref document: A1 Designated state(s): BW GH GM KE LS MW MZ NA SD SL SZ TZ UG ZM ZW AM AZ BY KG KZ MD RU TJ TM AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LT LU MC NL PL PT RO SE SI SK TR BF BJ CF CG CI CM GA GN GQ GW ML MR NE SN TD TG |
|
121 | Ep: the epo has been informed by wipo that ep was designated in this application | ||
WWE | Wipo information: entry into national phase |
Ref document number: 3985/DELNP/2006 Country of ref document: IN |
|
WWE | Wipo information: entry into national phase |
Ref document number: 2007161428 Country of ref document: US Ref document number: 10586185 Country of ref document: US Ref document number: 200580002452.2 Country of ref document: CN |
|
NENP | Non-entry into the national phase |
Ref country code: DE |
|
WWW | Wipo information: withdrawn in national office |
Ref document number: DE |
|
WWE | Wipo information: entry into national phase |
Ref document number: 2005703556 Country of ref document: EP |
|
WWP | Wipo information: published in national office |
Ref document number: 2005703556 Country of ref document: EP |
|
WWP | Wipo information: published in national office |
Ref document number: 10586185 Country of ref document: US |