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WO2018168625A1 - Joint homocinétique à bille fixe utilisé dans un arbre d'entraînement de roue arrière - Google Patents

Joint homocinétique à bille fixe utilisé dans un arbre d'entraînement de roue arrière Download PDF

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Publication number
WO2018168625A1
WO2018168625A1 PCT/JP2018/008920 JP2018008920W WO2018168625A1 WO 2018168625 A1 WO2018168625 A1 WO 2018168625A1 JP 2018008920 W JP2018008920 W JP 2018008920W WO 2018168625 A1 WO2018168625 A1 WO 2018168625A1
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WO
WIPO (PCT)
Prior art keywords
ball
joint member
velocity universal
constant velocity
universal joint
Prior art date
Application number
PCT/JP2018/008920
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English (en)
Japanese (ja)
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WO2018168625A8 (fr
Inventor
智茂 小林
正純 小林
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Ntn株式会社
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Filing date
Publication date
Application filed by Ntn株式会社 filed Critical Ntn株式会社
Publication of WO2018168625A1 publication Critical patent/WO2018168625A1/fr
Publication of WO2018168625A8 publication Critical patent/WO2018168625A8/fr

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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
    • 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

Definitions

  • the present invention relates to a fixed type constant velocity universal joint, and more particularly to a fixed type constant velocity universal joint used for a drive shaft for a rear wheel of an automobile.
  • a drive shaft of an automobile is composed of an outboard constant velocity universal joint attached to a wheel, an inboard constant velocity universal joint attached to a differential gear, and an intermediate shaft connecting both constant velocity universal joints.
  • a fixed type constant velocity universal joint that can take a large operating angle but is not displaced in the axial direction is used as the constant velocity universal joint on the outboard side.
  • a slidable constant velocity universal joint that can be displaced in the axial direction while having a relatively small maximum operating angle is used.
  • the drive shaft includes a front wheel drive shaft attached to the front wheel and a rear wheel drive shaft attached to the rear wheel. Since the fixed type constant velocity universal joint on the outboard side of the front wheel drive shaft is attached to the front wheel which is a steering wheel, one having a large maximum operating angle (for example, 45 ° or more) is used. On the other hand, the fixed constant velocity universal joint on the outboard side of the rear wheel drive shaft is attached to the rear wheel that is not steered, so that the maximum operating angle is smaller than the fixed constant velocity universal joint of the front wheel drive shaft. .
  • fixed constant velocity universal joints having the same specifications are used for the front wheel drive shaft and the rear wheel drive shaft from the viewpoint of mass production costs and the like. That is, a fixed constant velocity universal joint with a high operating angle used for the front wheel drive shaft is also used for the rear wheel drive shaft.
  • a zeppa type constant velocity universal joint As a typical fixed type constant velocity universal joint, there is a zeppa type constant velocity universal joint.
  • the center of curvature of the track groove of the outer joint member and the center of curvature of the track groove of the inner joint member are offset by an equal distance on the opposite side in the axial direction with respect to the joint center.
  • the ball is always held within the bisector of the operating angle, and uniform velocity is ensured between the outer joint member and the inner joint member.
  • a zeppa type constant velocity universal joint usually has six torque transmission balls.
  • Patent Document 1 the number of torque transmission balls of a zepper type constant velocity universal joint is eight. It is shown. By making the number of balls 8 in this way, lightness and compactness are achieved while ensuring strength, load capacity, and durability equal to or higher than those of a zeppa type constant velocity universal joint with six balls. be able to.
  • Patent Document 2 shows a rear wheel drive shaft.
  • this rear wheel drive shaft by increasing the spline diameter provided at both ends of the intermediate shaft (hollow shaft), the hollow shaft has a sufficient strength, so that it can be thinned. Weight reduction is achieved.
  • the zeppa type constant velocity universal joint provided with eight balls as shown in Patent Document 1 is put into practical use as a mass-produced product.
  • the present invention examines further reduction in weight and size of this type of fixed constant velocity universal joint.
  • Patent Document 2 The invention proposed in Patent Document 2 is aimed at reducing the weight and increasing the strength of the hollow shaft used for the drive shaft for the rear wheel.
  • this document does not mention the problem of making the fixed type constant velocity universal joint lightweight and compact.
  • the problem to be solved by the present invention is that a fixed type constant velocity universal joint used for a drive shaft for a rear wheel, particularly an eight-ball zepper type constant velocity universal joint, can be further improved by examining internal specifications.
  • the goal is to reduce weight and size.
  • the present invention is a fixed type constant velocity universal joint used for a drive shaft for a rear wheel, wherein eight track grooves extending in the axial direction are formed on a spherical inner peripheral surface.
  • eight pockets for accommodating the balls and formed on the outer peripheral surface of the outer joint member and the outer peripheral surface of the inner joint member.
  • a cage that is in sliding contact, and the center of curvature of the track groove of the outer joint member and the center of curvature of the track groove of the inner joint member are offset by an equal distance on the opposite side in the axial direction with respect to the joint center.
  • of Pitch circle diameter PCD BALL and the ratio PCD BALL / D BALL of the diameter D BALL of the ball is 3.70 to 3.87, wherein the axial length W I ⁇ TRUCK track grooves of the inner joint member
  • a fixed type constant velocity universal joint having a ratio W I ⁇ TRUCK / D BALL of the ball diameter D BALL of 1.1 to 1.3.
  • each member such as the radial thickness of the inner joint member (specifically, the groove bottom of the track groove of the inner joint member and the pitch circle of the spline hole, without causing a decrease in load capacity or durability) ) In the radial direction).
  • the track grooves formed on the outer peripheral surface of the inner joint member can be brought closer to the inner diameter side, so that the pitch circle diameter of the track grooves, that is, the pitch circle diameter of the balls arranged in the track grooves, It can be made smaller than the 8-ball zeppa type constant velocity universal joint having a high operating angle applicable to both the front wheel drive shaft and the rear wheel drive shaft.
  • the fixed type constant velocity universal joint can be made compact in the radial direction to reduce the weight.
  • FIG. 7 shows a state in which the fixed type constant velocity universal joint 3 according to the present invention has a maximum operating angle (20 °)
  • FIG. 8 shows a state in which the fixed type constant velocity universal joint 3 ′ according to the comparative product operates at maximum. The state where the angle (47 °) is taken is shown.
  • the fixed type constant velocity universal joint is dedicated to the rear wheel drive shaft and the maximum operating angle is reduced, so that the amount of axial movement of the ball relative to the inner joint member is reduced, and the track groove and ball Therefore, the length of the track groove of the inner joint member in the axial direction can be shortened. Thereby, an inner joint member can be made compact in an axial direction, and weight reduction can be achieved.
  • the internal specification of the constant velocity universal joint according to the torque load capacity (that is, the size of the constant velocity universal joint) can be represented by expressing the dimensions of the respective members as a ratio to the ball diameter.
  • the fixed type constant velocity universal joint is exclusively used for the rear wheel drive shaft and the maximum operating angle is reduced.
  • the dimensions of each member relative to the ball diameter ⁇ specifically, the pitch diameter of the ball relative to the ball diameter (PCD BALL / D BALL ) and the axial length of the track groove of the inner joint member (W I ⁇ TRUCK / D BALL ) ⁇ are smaller than conventional products, a new lightweight and compact series of fixed type constant velocity universal joints Can be built.
  • the ratio W C / D BALL between the axial width W C of the cage and the ball diameter D BALL can be set to 1.63 to 1.80.
  • the ratio W I / D BALL between the axial width W I of the inner joint member and the ball diameter D BALL can be set to 1.40 to 1.55.
  • the axis of the inner joint member 102 and the axis of the cage 104 are orthogonal to each other, and in this state, the inner joint member 102 was slid in the axial direction of the cage 104 and inserted into the inlet 104a of the cage 104.
  • the inner joint member 102 in order to incorporate the inner joint member 102 into the inner periphery of the cage 104, it is necessary to make the inner diameter B of the inlet portion 104a of the cage 104 larger than the maximum width C of the outer diameter surface 102a of the inner joint member 102. Yes (B> C). For this reason, the radial thickness at the inlet 104a of the cage 104 is reduced, and the strength of this portion may be insufficient.
  • the axial length of the track groove of the inner joint member can be shortened as described above by reducing the maximum operating angle.
  • the inner joint member The track groove axial length W I ⁇ TRUCK can be made smaller than the circumferential length L P of each pocket of the cage (see FIG. 10).
  • the protrusions between the track grooves of the inner joint member are inserted into the cage pocket from the inner diameter side, while the inner circumference of the cage is An inner joint member can be incorporated (see FIG. 11).
  • the thickness in the radial direction of the cage can be made substantially uniform in the circumferential direction to ensure the strength. .
  • the above-mentioned fixed type constant velocity universal joint can have a maximum operating angle of 20 ° or less.
  • the internal specifications ((the pitch diameter of the ball with reference to the ball diameter and By setting the axial length of the track groove of the inner joint member, it is possible to further reduce the weight and size while maintaining the torque load capacity.
  • FIG. 4 is a longitudinal sectional view of a sliding type constant velocity universal joint incorporated in the rear wheel drive shaft (cross sectional view taken along line XX in FIG. 3B). It is a transverse cross section of the above-mentioned sliding type constant velocity universal joint (sectional view in the joint central plane of Drawing 3A).
  • FIG. 4 is a longitudinal sectional view of a fixed type constant velocity universal joint incorporated in the rear wheel drive shaft (cross sectional view taken along line YY in FIG. 4B). It is a cross-sectional view of the fixed type constant velocity universal joint (cross-sectional view in the joint center plane of FIG.
  • FIG. 1 shows a power transmission mechanism of an independent suspension type rear wheel drive vehicle (for example, an FR vehicle).
  • the rotational driving force output from the engine E is transmitted to the differential gear G via the transmission M and the propeller shaft PS, and from there to the left and right rear wheels via the left and right rear wheel drive shaft 1. Is transmitted to (wheel W).
  • the rear wheel drive shaft 1 includes a sliding type constant velocity universal joint 2 that allows both axial displacement and angular displacement on the inboard side (right side in the drawing), and the outboard side (see FIG.
  • a fixed type constant velocity universal joint 3 that allows only angular displacement is provided on the middle left side, and both the constant velocity universal joints 2 and 3 are connected by an intermediate shaft 4.
  • the sliding constant velocity universal joint 2 on the inboard side is connected to the differential gear G, and the fixed constant velocity universal joint 3 on the outboard side is connected to the wheels W (see FIG. 1).
  • the sliding type constant velocity universal joint 2 is attached to the outer joint member 21 attached to the differential gear G (see FIG. 1) and the inboard side end of the intermediate shaft 4 (see FIG. 2).
  • the outer joint member 21 includes a cup-shaped mouth portion 21a having an opening in the axial direction ⁇ outboard side, left side in FIG. 3A ⁇ and the other axial end ⁇ inboard side, FIG. In A), it integrally has a stem portion 21b extending to the right side ⁇ . Eight linear track grooves 21d extending in the axial direction are provided on the cylindrical inner peripheral surface 21c of the mouse portion 21a. A spline 21e to be inserted into the spline hole of the differential gear G is provided on the outer peripheral surface of the end portion on the inboard side of the stem portion 21b.
  • mouth part 21a and the stem part 21b may be joined by welding etc., after forming these separately in addition to integrally forming with the same material.
  • a spline hole 22c into which the intermediate shaft 4 is inserted is provided at the axis of the inner joint member 22.
  • Eight linear track grooves 22e extending in the axial direction are provided on the spherical outer peripheral surface 22d of the inner joint member 22. That is, the inner joint member 22 integrally includes a cylindrical portion 22a having a spline hole 22c and a plurality of protruding portions 22b protruding from the cylindrical portion 22a to the outer diameter, and between the circumferential directions of the plurality of protruding portions 22b.
  • a track groove 22e is provided. The outer diameter surfaces of the plurality of projecting portions 22 b become the spherical outer peripheral surface 22 d of the inner joint member 22.
  • the track groove 21d of the outer joint member 21 and the track groove 22e of the inner joint member 22 are opposed to each other in the radial direction to form eight ball tracks, and one ball 23 is arranged on each ball track.
  • the cross-sectional shape of the track grooves 21d and 22e is an elliptical shape or a Gothic arch shape. As a result, the track grooves 21d and 22e and the ball 23 are in contact with a so-called angular contact that has a contact angle of about 30 to 45 °. Is done.
  • the cross-sectional shape of the track grooves 21d and 22e may be an arc shape, and the track grooves 21d and 22e and the ball 23 may be so-called circular contacts.
  • the holder 24 has eight pockets 24a for holding the balls 23.
  • the eight pockets 24a all have the same shape and are arranged at equal intervals in the circumferential direction.
  • the outer peripheral surface of the cage 24 is provided with a spherical portion 24b that is in sliding contact with the cylindrical inner peripheral surface 21c of the outer joint member 21, and a conical portion 24c that extends tangentially from both axial ends of the spherical portion 24b.
  • the conical portion 24c is a stopper that restricts the contact angle of the sliding type constant velocity universal joint 2 with the inner peripheral surface 21c of the outer joint member 21 from being increased further when the sliding joint constant velocity universal joint 2 takes the maximum operating angle. Function as.
  • the inclination angle of the conical portion 24 c with respect to the axial center of the cage 24 is set to a value that is 1 ⁇ 2 of the maximum operating angle of the sliding type constant velocity universal joint 2.
  • a spherical surface portion 24d that is in sliding contact with the spherical outer peripheral surface 22d of the inner joint member 22 is provided.
  • the center of curvature O 24b of the spherical surface portion 24b of the outer peripheral surface of the cage 24 and the center of curvature O 24d of the spherical surface portion 24d of the inner peripheral surface of the cage 24 (that is, the center of curvature of the spherical outer peripheral surface 22d of the inner joint member 22). are offset by an equal distance on the opposite side in the axial direction with respect to the joint center O (s).
  • the curvature center O 24b of the spherical surface portion 24b of the outer peripheral surface of the cage 24 is offset to the inboard side (joint back side) with respect to the joint center O (s), and the spherical surface of the inner circumferential surface of the cage 24 center of curvature O 24d parts 24d is offset to the outboard side (joint opening side) with respect to the joint center O (s).
  • the ball 23 held by the cage 24 is always disposed within the bisector of the operating angle at an arbitrary operating angle, and constant velocity between the outer joint member 21 and the inner joint member 22 is ensured. Secured.
  • the fixed type constant velocity universal joint 3 includes an outer joint member 31 attached to the wheel W (see FIG. 1) and an inner side attached to the outboard side end portion of the intermediate shaft 4 (see FIG. 2).
  • a joint member 32, eight balls 33 that transmit torque between the outer joint member 31 and the inner joint member 22, and a cage 34 that holds the eight balls 33 are provided.
  • the outer joint member 31 includes a cup-shaped mouth portion 31a having an opening in one axial direction ⁇ inboard side, right side in FIG. 4A ⁇ and the other axial end ⁇ outboard side, FIG. A) is integrally provided with a stem portion 31b extending to the left side ⁇ .
  • a stem portion 31b extending to the left side ⁇ .
  • eight arc-shaped track grooves 31d extending in the axial direction are formed. Each track groove 31d extends to the opening side end face of the mouse portion 31a. That is, a slight chamfered portion necessary for processing is provided between the track groove 31d of the outer joint member 31 and the opening side end surface of the mouth portion 31a, but in order to incorporate the ball as in the comparative product.
  • the necessary tapered surface K1 ⁇ see FIG. 5A ⁇ is not provided. Further, at the opening end of the inner peripheral surface 31c of the outer joint member 31, a tapered surface K2 that abuts against the intermediate shaft and defines the maximum operating angle of the fixed type constant velocity universal joint as in the comparative product ⁇ FIG. (A) Reference ⁇ is not provided.
  • a spline 31e to be inserted into the spline hole on the wheel W side is provided on the outer peripheral surface of the stem portion 31b.
  • mouth part 31a and the stem part 31b may be joined by welding etc., after forming these separately in addition to integrally forming with the same material. Moreover, you may form the through-hole of an axial direction in the axial center of the mouse
  • a spline hole 32c into which the intermediate shaft 4 is inserted is provided at the axis of the inner joint member 32.
  • eight arc-shaped track grooves 32e extending in the axial direction are provided.
  • the inner joint member 32 integrally includes a cylindrical portion 32a having a spline hole 32c and a plurality of protruding portions 32b protruding from the cylindrical portion 32a to the outer diameter, and between the circumferential directions of the plurality of protruding portions 32b.
  • a track groove 32e is provided.
  • the outer diameter surfaces of the plurality of projecting portions 32 b become spherical outer peripheral surfaces 32 d of the inner joint member 32.
  • the track groove 31d of the outer joint member 31 and the track groove 32e of the inner joint member 32 face each other in the radial direction to form eight ball tracks, and one ball 33 is arranged on each ball track.
  • the cross-sectional shape of the track grooves 31d and 32e is an elliptical shape or a Gothic arch shape, so that the track grooves 31d and 32e and the ball 33 are in contact with a so-called angular contact with a contact angle of about 30 to 45 °. Is done.
  • the cross-sectional shape of the track grooves 31d and 32e may be an arc shape, and the track grooves 31d and 32e and the ball 33 may be so-called circular contacts.
  • the curvature center O 31d of the track groove 31 d of the outer joint member 31 is offset to the inboard side (joint opening side) with respect to the joint center O (f), and the curvature of the track groove 32 e of the inner joint member 32 is.
  • the center O 32e is offset to the outboard side (the joint back side) with respect to the joint center O (f).
  • the holder 34 has eight pockets 34 a for holding the balls 33.
  • the eight pockets 34a all have the same shape and are arranged at equal intervals in the circumferential direction.
  • the spherical outer peripheral surface 34 b of the cage 34 is in sliding contact with the spherical inner peripheral surface 31 c of the outer joint member 31.
  • the spherical inner peripheral surface 34 c of the cage 34 is in sliding contact with the spherical outer peripheral surface 32 d of the inner joint member 32.
  • Center of curvature of outer peripheral surface 34b of cage 34 ie, center of curvature of spherical inner peripheral surface 31c of outer joint member 31
  • center of curvature of inner peripheral surface 34c ie, spherical outer peripheral surface of inner joint member 32
  • 32d curvature center coincides with the joint center O (f).
  • the intermediate shaft 4 a hollow shaft having an axial through hole 41 can be used as shown in FIG. 2.
  • the intermediate shaft 4 includes a large diameter portion 42 provided at the center in the axial direction, a small diameter portion 43 provided at both ends in the axial direction, and a tapered portion 44 that continues the large diameter portion 42 and the small diameter portion 43.
  • the small-diameter portion 43 of the intermediate shaft 4 is provided with an annular groove 45 and a spline 46 for boot mounting.
  • the outer diameter of the small diameter portion 43 is constant except for the annular groove 45 and the spline 46.
  • the intermediate shaft 4 is not limited to a hollow shaft, and a solid shaft can also be used.
  • the spline 46 at the end on the inboard side of the intermediate shaft 4 is press-fitted into the spline hole 22 c of the inner joint member 22 of the sliding type constant velocity universal joint 2.
  • the intermediate shaft 4 and the inner joint member 22 are connected so as to be able to transmit torque by spline fitting.
  • An annular groove is formed at the end of the intermediate shaft 4 on the inboard side, and a retaining ring 47 is attached to the groove.
  • the spline 46 at the end on the outboard side of the intermediate shaft 4 is press-fitted into the spline hole 32 c of the inner joint member 32 of the fixed type constant velocity universal joint 3. Thereby, the intermediate shaft 4 and the inner joint member 32 are connected so as to be able to transmit torque by spline fitting.
  • An annular groove is formed at the end of the intermediate shaft 4 on the outboard side, and a retaining ring 47 is attached to the groove.
  • the above-mentioned sliding type constant velocity universal joint 2 and fixed type constant velocity universal joint 3 are exclusively used for the rear wheel drive shaft. Therefore, the maximum operating angle is smaller than that of the conventional product that can also be used for the front wheel drive shaft. Can be set. In this embodiment, the maximum operating angles of the sliding type constant velocity universal joint 2 and the fixed type constant velocity universal joint 3 are both set to 20 ° or less. Accordingly, it is possible to reduce the weight and size of the sliding type constant velocity universal joint 2 and the fixed type constant velocity universal joint 3 while maintaining the load capacity.
  • the internal specifications of the fixed type constant velocity universal joint 3 will be described in detail.
  • the internal specifications of the fixed type constant velocity universal joint 3 according to the present invention are shown in the following Table 1, FIG. 5 and FIG. 6 as a comparative product having the same ball diameter (eight ball zepper type constant velocity with a maximum operating angle of 47 °). It is shown in comparison with a universal joint.
  • 5 and 6 are sectional views of the fixed type constant velocity universal joint 3 according to the present invention, and the lower half is a sectional view of the fixed type constant velocity universal joint 3 'according to the comparative product. is there.
  • Each part of the comparative product is given a reference numeral with “′ (dash)” added to the part of the product of the present invention.
  • PCD PCD BALL connecting the center of curvature center of the track groove 32e of the center of curvature of the track grooves 31d of the outer joint member 31 O 31d or the inner joint member 32 O 32e and the ball 33
  • Inner ring track length (axial length of track groove of inner joint member) W I ⁇ TRUCK Strictly speaking, it is the axial length of the contact locus between track groove 32e of inner joint member 32 and ball 33 However, in this specification, it refers to the axial length of the spherical outer peripheral surface 32d of the inner joint member 32, that is, the axial distance between the end surfaces extending from the both axial ends of the outer peripheral surface 32d to the inner diameter side.
  • Inner ring width (axial width of the inner joint member) W I The maximum axial dimension of the inner joint member 32. In the illustrated example, the inner ring width is the axial distance between both end faces of the cylindrical portion 32a of the inner joint member 32. is there.
  • Thickness of inner ring (radial thickness of inner joint member) T I : groove bottom and spline hole of track groove 32e in joint center plane P ⁇ plane passing through joint center O (f) and perpendicular to axis ⁇ The radial distance from the pitch circle of 32c.
  • Spline PCD Peak circle diameter of spline hole of inner joint member
  • PCD SPL Diameter of meshing pitch circle between spline hole 32c of inner joint member 32 and spline 46 of intermediate shaft 4.
  • Outer ring outer diameter D O The maximum outer diameter of the outer joint member 31.
  • Joint center to outer ring opening end face length W1 O A distance in the axial direction between the joint center O (f) and the opening-side end face (end face on the inboard side) of the mouth portion 31a of the outer joint member 31.
  • Cage thickness T C A radial thickness in the joint center plane P of the cage 34.
  • Cage width W C The maximum dimension in the axial direction of the cage 34, and the axial distance between both end faces of the cage 34 in the illustrated example.
  • the maximum load applied to each ball 33 increases as the operating angle increases. Therefore, the maximum load applied to each ball 33 decreases by reducing the maximum operating angle as described above. As a result, there is a margin in the strength of the inner joint member 32 in contact with the ball 33, so that the radial thickness of the inner joint member 32 can be reduced while maintaining the same durability as the comparative product ⁇ T I ⁇ T I ', see (1) in Table 1 above ⁇ .
  • the pitch diameter of the track grooves 32e of the inner joint member 32 that is, the balls 33 arranged in the track grooves 32e, without reducing the load capacity and durability.
  • the fixed type constant velocity universal joint 3 can be made compact in the radial direction, and light weight can be achieved.
  • the inside of the pocket 34a of the cage 34 can be reduced by reducing the maximum operating angle of the fixed type constant velocity universal joint 3.
  • the movement amount of the ball 33 in the radial direction becomes small. Also from this viewpoint, the thickness of the cage 34 in the radial direction can be reduced.
  • the fixed type constant velocity universal joint 3 can be reduced in weight and size while securing the ball 33 to prevent the ball 33 from climbing onto the track groove edge.
  • FIG. 7 shows a state in which the fixed type constant velocity universal joint 3 according to the present invention has a maximum operating angle (20 °)
  • FIG. 8 shows a state in which the fixed type constant velocity universal joint 3 ′ according to the comparative product operates at maximum.
  • the state where the angle (47 °) is taken is shown.
  • the length of the contact locus L1 between the track groove 32e of the inner joint member 32 and the ball 33 in the product of the present invention is the length of the track groove 32e 'and ball 33 of the inner joint member 32' in the comparative product. It is shorter than the length of the contact locus L1 with “.
  • the length of the contact locus L2 between the track groove 31d of the outer joint member 31 and the ball 33 in the product of the present invention is the track groove 31d ′ of the outer joint member 31 ′ in the comparative product.
  • the length of the contact locus L2 ′ between the ball 33 ′ and the ball 33 ′ is shortened.
  • the axial length of the opening side portion from the joint center O (f) of the track groove 31d, specifically, from the joint center O (f) to the opening side end surface of the mouth portion 31a of the outer joint member 31. Can be shortened ⁇ W1 O ⁇ W1 O ', see (7) in Table 1 above ⁇ .
  • the outer joint member 31 can be made compact in the axial direction to reduce the weight.
  • the ratio D O / PCD SPL between the outer diameter D O of the outer joint member 31 and the pitch circle diameter PCD SPL of the spline hole 32c of the inner joint member 32 can be made smaller than that of the comparative product.
  • the pitch circle of the fitting portion between the spline hole 32c of the inner joint member 32 and the spline 46 (see FIG. 2) of the intermediate shaft 4 is increased. Since the diameter is increased, the surface pressure at the contact portion between the spline teeth is reduced. Thereby, since the axial direction length of the spline hole 32c of the inner joint member 32 can be shortened while maintaining the surface pressure per spline tooth, the axial width of the cylindrical portion 32a of the inner joint member 32 can be reduced. It can be shortened.
  • the axial length of the track groove 32 e of the inner joint member 32 can be shortened.
  • the axial length W I ⁇ TRUCK of the track groove 32e (see FIG. 6) of the inner joint member 32 (that is, from both axial ends of the outer peripheral surface 32d of the inner joint member 32).
  • the axial distance between the end faces extending toward the inner diameter side) is made shorter than the circumferential length L P of the pocket 34a of the cage 34 (specifically, the distance between the wall surfaces facing the circumferential direction of the pocket 34a).
  • the inner joint member 32 when the inner joint member 32 is incorporated into the inner periphery of the cage 34, the inner joint member 32 is placed in a state where the axis of the cage 34 and the axis of the inner joint member 32 are orthogonal to each other as shown in FIG. 11.
  • the protrusion 32b can be inserted into the pocket 34a of the cage 34 from the inner diameter side.
  • the inner joint member 32 can be incorporated in the inner periphery of the retainer 34 while avoiding interference with the retainer 34 even when the radial thickness of the retainer 34 is substantially uniform throughout the entire axial direction. it can. Therefore, since it is not necessary to form a thin portion for incorporating the inner joint member 32 at the axial end of the cage 34, the strength of the cage 34 can be ensured.
  • the present invention considers various conditions obtained by reducing the maximum operating angle of the constant velocity universal joint, and examines the internal specifications of the constant velocity universal joint.
  • the constant velocity universal joint is lighter and more compact while maintaining torque load capacity. This makes it possible to build a new series of lightweight and compact fixed constant velocity universal joints that can be used exclusively for the rear wheel drive shaft.
  • the fixed type constant velocity universal joint described above is not limited to a rear wheel drive shaft (for example, an FR vehicle) that is driven only by rear wheels, but is a rear wheel drive shaft for four-wheel drive vehicles (in particular, It can also be used in a four-wheel drive vehicle in which the rear wheels are main drive wheels.
  • the fixed type constant velocity universal joint is preferably applied to a rear wheel drive shaft for a rear wheel drive or four wheel drive passenger car.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
  • Handcart (AREA)
  • Arrangement And Driving Of Transmission Devices (AREA)
  • Rolling Contact Bearings (AREA)

Abstract

Joint homocinétique fixe (3) équipé d'un élément de joint extérieur (31), d'un élément de joint intérieur (32), de huit billes (33) et d'une cage (34). Le centre de courbure (O31d) de la rainure de piste (31d) de l'élément de joint extérieur (31) et le centre de courbure (O32e) de la rainure de piste (32e) de l'élément de joint intérieur (32) sont chacun décalés du centre de joint (O(f)) de distances égales sur des côtés opposés du centre de joint (O(f)) dans la direction axiale. Le rapport (PCDBALL)/(DBALL) du diamètre de cercle primitif (PCDBALL) des billes (33) et du diamètre (DBALL) de chaque bille (33) est de 3,70 à 3,87. En outre, le rapport (WI·TRUCK/DBALL) de la longueur dans la direction axiale (WI·TRUCK) de la rainure de piste (32e) de l'élément de joint intérieur (32) et du diamètre (DBALL) de chaque bille est de 1,1 à 1,3.
PCT/JP2018/008920 2017-03-17 2018-03-08 Joint homocinétique à bille fixe utilisé dans un arbre d'entraînement de roue arrière WO2018168625A1 (fr)

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JP2017-052641 2017-03-17
JP2017052641A JP6736509B2 (ja) 2017-03-17 2017-03-17 後輪用ドライブシャフトに用いられる固定式等速自在継手

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WO2018168625A8 WO2018168625A8 (fr) 2019-09-26

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Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2009041280A1 (fr) * 2007-09-26 2009-04-02 Ntn Corporation Joint homocinétique fixe
WO2011149005A1 (fr) * 2010-05-27 2011-12-01 Ntn株式会社 Joint universel homocinétique fixé
JP2014084952A (ja) * 2012-10-24 2014-05-12 Ntn Corp 固定式等速自在継手
WO2014208242A1 (fr) * 2013-06-26 2014-12-31 Ntn株式会社 Joint homocinétique de type fixe

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2009041280A1 (fr) * 2007-09-26 2009-04-02 Ntn Corporation Joint homocinétique fixe
WO2011149005A1 (fr) * 2010-05-27 2011-12-01 Ntn株式会社 Joint universel homocinétique fixé
JP2014084952A (ja) * 2012-10-24 2014-05-12 Ntn Corp 固定式等速自在継手
WO2014208242A1 (fr) * 2013-06-26 2014-12-31 Ntn株式会社 Joint homocinétique de type fixe

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JP2018155319A (ja) 2018-10-04
JP6736509B2 (ja) 2020-08-05
WO2018168625A8 (fr) 2019-09-26

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