WO2019194046A1 - Joint homocinétique de type fixe - Google Patents

Joint homocinétique de type fixe Download PDF

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Publication number
WO2019194046A1
WO2019194046A1 PCT/JP2019/013212 JP2019013212W WO2019194046A1 WO 2019194046 A1 WO2019194046 A1 WO 2019194046A1 JP 2019013212 W JP2019013212 W JP 2019013212W WO 2019194046 A1 WO2019194046 A1 WO 2019194046A1
Authority
WO
WIPO (PCT)
Prior art keywords
joint member
peripheral surface
track groove
spherical
ball
Prior art date
Application number
PCT/JP2019/013212
Other languages
English (en)
Japanese (ja)
Other versions
WO2019194046A8 (fr
Inventor
輝明 藤尾
雅司 船橋
Original Assignee
Ntn株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from JP2019048306A external-priority patent/JP7139269B2/ja
Application filed by Ntn株式会社 filed Critical Ntn株式会社
Priority to DE112019001761.6T priority Critical patent/DE112019001761T5/de
Priority to CN201980022715.8A priority patent/CN111919044B/zh
Priority to US17/041,206 priority patent/US11927226B2/en
Publication of WO2019194046A1 publication Critical patent/WO2019194046A1/fr
Publication of WO2019194046A8 publication Critical patent/WO2019194046A8/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
    • F16D3/2233—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 track is made up of two curves with a point of inflexion in between, i.e. S-track 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
    • 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
    • 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

  • This invention relates to a fixed type constant velocity universal joint.
  • the constant velocity universal joint that constitutes the power transmission system of automobiles and various industrial machines connects the two shafts on the drive side and the driven side so that torque can be transmitted, and transmits rotational torque at a constant speed even if the two shafts have an operating angle. can do.
  • Constant velocity universal joints are broadly classified into fixed constant velocity universal joints that allow only angular displacement and sliding constant velocity universal joints that allow both angular displacement and axial displacement.
  • a sliding type constant velocity universal joint is used on the differential side (inboard side), and a fixed type constant velocity universal joint is used on the drive wheel side (outboard side).
  • the maximum operating angle is generally 47 ° for Rzeppa constant velocity universal joints (BJ type) and 50 ° for undercut free constant velocity universal joints (UJ type). From the viewpoint of improving the turning ability, demands exceeding 50 ° are increasing. In order to meet these requirements, fixed constant velocity universal joints having various structures have been proposed.
  • Patent Document 1 discloses a fixed type constant velocity universal joint having a structure in which each track groove of the outer joint member and the inner joint member is a combination of an arc shape and a taper shape, and the operating angle can be increased without increasing the outer diameter. Proposed.
  • Patent Document 2 in a conventional fixed constant velocity universal joint, a phase angle (phase angle) at which a torque transmission ball (hereinafter also simply referred to as a ball) moves most toward the opening side of an outer joint member at the maximum operating angle. 0 °), the ratio of the axial parallel distance between the center of the ball and the joint center and the axial parallel distance between the center of the ball and the open conical surface of the outer joint member is less than 2.9. It is said that the function can be maintained. Further, when the ball protrudes from the track groove of the outer joint member at an operating angle until the contact point is lost, the functionality can be maintained by setting the ratio to less than 2.2.
  • Patent Document 3 describes a mode in which each spherical edge of the outer joint member and the inner joint member bites into the cage and shears when the fixed type constant velocity universal joint takes a high operating angle. This is because, in the longitudinal section of the fixed type constant velocity universal joint having the maximum operating angle, the contact point between the spherical outer peripheral surface of the cage and the edge portion of the spherical inner peripheral surface of the outer joint member, and the spherical inner peripheral surface of the cage The strength of the cage can be ensured by making the angle formed between the straight line connecting the contact point with the edge of the spherical outer peripheral surface of the inner joint member and the center line of the cage 10 ° or less.
  • Patent Document 2 does not pay attention to the strength problem of the cage in the fixed type constant velocity universal joint having such an operation mode.
  • the cage is in a sheared state because the ball when the high operating angle is taken pushes the cage toward the opening side of the constant velocity universal joint. This occurs due to being pressed against the joint member.
  • the width of the inner joint member is widened to be incorporated into the cage.
  • the retainer may not be established because the built-in spigot diameter of the retainer becomes too large.
  • problems such as weight increase.
  • the present invention is a fixed type constant velocity universal joint having an operation form in which a ball is removed from a track groove and loses a contact point by taking a high operating angle, and a spherical edge of an outer joint member and an inner joint member
  • An object of the present invention is to provide a fixed type constant velocity universal joint capable of suppressing a mode of shear fracture caused by biting into a cage and capable of suppressing an increase in weight.
  • the present inventors have found that the torque transmission ball that is not in contact with the track groove of the outer joint member at the high operating angle returns to the end of the track groove on the opening side. Focusing on the fact that the track load is large when the contact state with the track groove is started, the present invention has been achieved by a new idea of ensuring the strength of the cage at this time.
  • the present invention provides an outer joint member having a plurality of track grooves extending in the longitudinal direction on the spherical inner peripheral surface and having an opening side and a back side that are spaced apart in the axial direction.
  • An inner joint member in which a plurality of track grooves extending substantially in the longitudinal direction on the spherical outer peripheral surface are formed to face the track grooves of the outer joint member, and a torque transmission ball incorporated between the opposed track grooves,
  • the torque transmission ball is held, and includes a spherical outer peripheral surface guided to the spherical inner peripheral surface of the outer joint member and a cage formed with a spherical inner peripheral surface guided to the spherical outer peripheral surface of the inner joint member.
  • the torque transmission ball moving toward the opening side of the track groove of the outer joint member has a phase angle ⁇ 2
  • the outer joint member starts to be out of contact with the track groove on the opening side of the track groove and returns to the track groove opening side end of the outer joint member at the phase angle ⁇ 1.
  • the projected end Eo in which the end on the opening side of the spherical inner peripheral surface of the outer joint member is vertically projected toward the spherical outer peripheral surface of the cage.
  • a projected end Ei obtained by projecting the end on the inner side of the spherical outer peripheral surface of the inner joint member in the vertical direction toward the spherical inner peripheral surface of the cage, at least partially in the axial direction of the cage Overlapping in It is characterized by.
  • the ratio Lt / Rm is set to 0.03 or more, where Lt is the length in the axial direction of the above-described overlapping portion of the cage, and Rm is the central radius of the radial thickness of the cage 5. It is desirable to set. Thereby, the shearing state of the column part can be sufficiently suppressed, and there is no problem in incorporating the inner joint member into the cage, and the weight can be suppressed.
  • the fixed type constant velocity universal joint in which the track groove of the outer joint member and the track groove of the inner joint member are inclined in the circumferential direction with respect to the axis of the joint, and a torque transmitting ball is incorporated at the intersection of the two track grooves. Is desirable. As a result, it is possible to realize a highly efficient fixed type constant velocity universal joint with less torque loss and heat generation while ensuring the strength of the cage.
  • the spherical edges of the outer joint member and the inner joint member bite into the cage. It is possible to realize a fixed type constant velocity universal joint capable of suppressing the mode of shear fracture due to the above and capable of suppressing an increase in weight.
  • FIG. 1 is a longitudinal sectional view of a fixed type constant velocity universal joint according to a first embodiment of the present invention.
  • 1b is a right side view of FIG.
  • FIG. 2 is an enlarged cross-sectional view of one torque transmission ball and a track groove on line PP in FIG. 1a. It is a longitudinal cross-sectional view when the fixed type constant velocity universal joint of FIG. 1a and FIG. 1b takes the maximum operating angle.
  • FIG. 3b is a right side view of FIG. 3a. It is the longitudinal cross-sectional view which expanded the H section of FIG. 3a.
  • FIG. 2 is a diagram showing a range in which a torque transmission ball is detached from a track groove of an outer joint member at a maximum operating angle, as shown in FIG.
  • FIG. 6 is a right side view showing a state in which the ball returns to the end of the outer joint member on the opening side of the track groove at the phase angle ⁇ 1 and starts contact with the track groove. It is the right view which showed the state when a torque transmission ball
  • FIG. 8A shows a longitudinal section of a fixed type constant velocity universal joint at the center in the circumferential direction of a pillar portion of the cage on the side where the phase angle is larger than the phase angle ⁇ 1 at which the torque transmission ball returns to the track groove of the outer joint member.
  • FIG. 11b is a right side view of FIG. 11a.
  • FIG. 13b is a right side view of FIG. 13a. It is a longitudinal cross-sectional view of the outer joint member of FIG. 13a.
  • FIG. 14b is a right side view of FIG. 14a.
  • 13b is a front view of the inner joint member of FIG. 13a.
  • FIG. 15b is a right side view of FIG. 15a.
  • FIG. 16b is a right side view of FIG. 16a. It is a longitudinal cross-sectional view of the current fixed type constant velocity universal joint.
  • FIG. 17b is a right side view of FIG. 17a.
  • FIG. 1a is a longitudinal sectional view of a fixed type constant velocity universal joint according to the first embodiment of the present invention
  • FIG. 1b is a right side view of FIG. 1a.
  • the fixed type constant velocity universal joint 1 of the present embodiment is based on a Rzeppa type constant velocity universal joint, and includes an outer joint member 2, an inner joint member 3, a torque transmission ball ( 4 and the cage 5 are the main components.
  • Eight curved track grooves 7 are formed on the spherical inner peripheral surface 6 of the outer joint member 2 at equal intervals in the circumferential direction and along the axial direction.
  • Eight curved track grooves 9 facing the track grooves 7 of the outer joint member 2 are formed on the spherical outer peripheral surface 8 of the inner joint member 3 at equal intervals in the circumferential direction and along the axial direction. .
  • Eight balls 4 for transmitting torque are incorporated one by one between the track groove 7 of the outer joint member 2 and the track groove 9 of the inner joint member 3.
  • a cage 5 that holds the ball 4 is disposed between the spherical inner peripheral surface 6 of the outer joint member 2 and the spherical outer peripheral surface 8 of the inner joint member 3. The ball 4 is accommodated in the pocket 5 a of the cage 5.
  • the spherical outer peripheral surface 12 of the cage 5 is slidably fitted to the spherical inner peripheral surface 6 of the outer joint member 2, and the spherical inner peripheral surface 13 of the cage 5 slides on the spherical outer peripheral surface 8 of the inner joint member 3. Fits freely.
  • ball trajectory centerline will be used to describe the shape and shape of the track groove extending substantially in the axial direction.
  • the ball trajectory center line means a locus drawn by the center of the ball when the ball arranged in the track groove moves along the track groove.
  • the centers of curvature of the spherical inner peripheral surface 6 of the outer joint member 2 and the spherical outer peripheral surface 8 of the inner joint member 3 are formed at the joint center O, respectively.
  • the curvature center O1 of the ball track center line X of the curved track groove 7 of the outer joint member 2 and the curvature center O2 of the ball track center line Y of the curved track groove 9 of the inner joint member 3 are , Offset from the joint center O by an equal distance f on the opposite side in the axial direction.
  • a female spline (spline includes serration; the same applies hereinafter) 11 is formed in the inner diameter hole 10 of the inner joint member 3, and the male spline 15 formed at the end of the intermediate shaft 14 (see FIG. 3a) is replaced with the female spline. 11 and coupled so that torque can be transmitted.
  • the inner joint member 3 and the intermediate shaft 14 are positioned in the axial direction by a retaining ring 16.
  • boots are attached to the outer periphery of the outer joint member 2 and the outer periphery of the intermediate shaft 14 connected to the inner joint member 3, and both ends of the boot are fastened and fixed by boot bands.
  • Grease as a lubricant is sealed inside the joint covered with boots.
  • a stem portion 2b is integrally formed on the bottom portion of the mouth portion 2a of the outer joint member 2, and the stem portion 2b is fitted with a hub wheel to which drive wheels are attached, although not shown.
  • a male spline and a threaded portion are formed.
  • FIG. 2 is an enlarged cross-sectional view of one ball and track groove on the line PP in FIG. 1a.
  • the cross-sectional shape of the track groove 7 of the outer joint member 2 and the track groove 9 of the inner joint member 3 is an elliptical shape or a Gothic arch shape, and as shown in FIG. Angular contact is made with the groove 7 at two points C1 and C2, and angular contact is made with the track groove 9 of the inner joint member 3 at two points C3 and C4.
  • the angle (contact angle ⁇ ) formed by the straight line passing through the center Ob of the ball 4 and each contact point C1, C2, C3, C4 and the straight line passing through the center Ob of the ball 4 and the joint center O (see FIG. 1a) is 30 ° or more. It is preferable to set to.
  • the cross-sectional shape of the track grooves 7 and 9 may be an arc shape, and the contact between the track grooves 7 and 9 and the ball 4 may be a circular contact.
  • the overall configuration of the fixed type constant velocity universal joint 1 of the present embodiment is as described above. Next, a characteristic configuration will be described.
  • the characteristic configuration of the fixed type constant velocity universal joint 1 of the present embodiment is summarized as follows. (1) When the maximum operating angle is taken, the ball 4 that moves most toward the opening side of the track groove 7 of the outer joint member 2 is the track groove 7 of the outer joint member 2 at the phase angle ⁇ 2 (see FIG. 5).
  • the track groove 7 starts to come out of the end portion on the opening side of the track member 7 and comes into a non-contact state with the track groove 7 and returns to the end portion on the opening side of the track groove 7 of the outer joint member 2 at the phase angle ⁇ 1 (see FIG. 5). It has an operation form to start a contact state with.
  • the opening-side end 6 a of the spherical inner peripheral surface 6 of the outer joint member 2 is a spherical edge on the opening side of the spherical inner peripheral surface 6, and the spherical inner peripheral surface 6.
  • the inlet chamfer 20 are directly connected to each other, which means a contact point between the spherical inner peripheral surface 6 and the inlet chamfer 20, and a cylindrical notch is provided between the spherical outer peripheral surface 6 and the inlet chamfer 20. In this case, it means a contact point between the spherical inner peripheral surface 6 and the notch.
  • the end 8a on the back side of the spherical outer peripheral surface 6 of the inner joint member 3 is a spherical edge on the back side of the spherical outer peripheral surface 8, and the spherical outer peripheral surface 8 and the back end surface are directly connected.
  • it means a contact point between the spherical outer peripheral surface 8 and the back end surface, and when a chamfer is provided between the spherical outer peripheral surface 8 and the back end surface, the contact point between the spherical outer peripheral surface 8 and the chamfered surface.
  • FIG. 17a is a longitudinal sectional view of an existing eight-ball type Rzeppa-type fixed constant velocity universal joint
  • FIG. 17b is a right side view of FIG. 17a.
  • the fixed type constant velocity universal joint 101 shown in FIGS. 17a and 17b has a maximum operating angle of 47 °.
  • the fixed type constant velocity universal joint 101 mainly includes an outer joint member 102, an inner joint member 103, a ball 104, and a cage 105.
  • the current Rzeppa-type fixed constant velocity universal joint 101 has an operation configuration in which the ball 104 is always in contact with the track groove 107 of the outer joint member 102 up to the maximum operating angle (47 °).
  • the inlet chamfer 120 provided at the opening end of the outer joint member 102 is not interfered by an intermediate shaft (not shown, the same as the intermediate shaft 14 in FIG. 3a) at the maximum operating angle, and the ball 104 and the outer
  • the contact state of the joint member 102 with the track groove 107 is set to be ensured. For this reason, the length L2 from the joint center O of the outer joint member 102 to the opening side end is set to be relatively long.
  • the intermediate shaft interferes with the inlet chamfer 120.
  • the inlet chamfer 120 is moved in the axial direction toward the joint center O.
  • the inclination angle is appropriately increased, and accordingly, it is necessary to shorten the length from the joint center O of the outer joint member 102 to the opening side end.
  • the fixed type constant velocity universal joint 1 of the present embodiment and the length L1 from the joint center O of the outer joint member 2 shown in FIG. The length is shorter than the length L2 from the joint center O of the outer joint member 102 of the fixed type constant velocity universal joint 101 to the opening side end.
  • the operation mode of the fixed type constant velocity universal joint 1 of the present embodiment that is, as shown in FIG.
  • the ball 4 that moves most toward the opening side of the track groove 7 of the outer joint member 2 moves from the opening side end of the track groove 7 of the outer joint member 2 at the phase angle ⁇ 2.
  • the operation mode is such that it comes off and starts the non-contact state with the track groove 7 and returns to the opening end of the track groove 7 of the outer joint member 2 at the phase angle ⁇ 1 and starts the contact state with the track groove 7.
  • FIG. 3a is a longitudinal sectional view of the fixed type constant velocity universal joint 1 shown in FIGS. 1a and 1b when the maximum operating angle is taken
  • FIG. 3b is a right side view of FIG. 3a
  • FIG. 4 is an enlarged longitudinal sectional view of a portion H in FIG. 3a.
  • FIG. 3A shows a state in which the axis Ni—Ni of the inner joint member 3 (intermediate shaft 14) is bent to the maximum operating angle ⁇ max (50 °) on the paper surface of the same figure with respect to the axis No-No of the outer joint member 2.
  • the axis Nc-Nc of the cage 5 is inclined at a bisecting angle ⁇ max / 2.
  • This phase angle is denoted as ⁇ 0 in this specification (see FIG. 3b).
  • the phase angle ⁇ is expressed in the manner of proceeding counterclockwise from the phase angle ⁇ 0.
  • the maximum operating angle is used to mean the maximum operating angle that the fixed type constant velocity universal joint 1 can tolerate during use.
  • the intermediate shaft 14 is shown in contact with the inlet chamfer 20 at the maximum operating angle.
  • the inlet chamfer 20 has an outer diameter of the intermediate shaft 14 at the maximum operating angle.
  • the inlet chamfer 20 functions as a stopper surface when the intermediate shaft 14 exceeds the maximum operating angle.
  • FIG. 4 shows the inlet chamfer 20 and the spherical inner peripheral surface 6 formed at the end of the outer joint member 2 on the opening side by broken lines.
  • a contact point locus connecting the contact point C2 (or C1, see FIG. 2) between the track groove 7 of the outer joint member 2 and the ball 4 in the axial direction is defined as CLo
  • the track groove 9 of the inner joint member 3 and the ball 4 The contact point trajectory connecting the contact point C3 (or C4, see FIG. 2) to the axial direction is CLi, and each is indicated by a broken line.
  • the contact point trajectories CLo and CLi are formed at positions away from the groove bottoms of the track grooves 7 and 9.
  • the contact point locus CLo extends in the axial direction toward the opening side of the outer joint member 2 and ends at the edge of the inlet chamfer 20.
  • the edge portion of the inlet chamfer 20 is an end portion on the opening side of the track groove 7 of the outer joint member 2.
  • the ball 4 deviates to the right in FIG. 4 with respect to the end of the contact point locus CLo, and the ball 4 and the track groove 7 are not in contact with each other.
  • the number of balls 4 that are not in contact with the track grooves 7 is one of eight, and the one ball 4 is not involved in torque transmission.
  • the contact point locus CLi of the track groove 9 of the inner joint member 3 extends to the position of the ball 4. That is, it is only necessary to secure the contact point locus CLi of the track groove 9 of the inner joint member 3 when the ball 4 moves to the end of the contact point locus CLo of the track groove 7 of the outer joint member 2.
  • the ball 4 is removed from the end of the outer joint member 2 on the opening side of the track groove 7 and is not in contact with the track groove 7, but the edge of the entrance chamfer 20 of the track groove 7 and the pocket 5 a of the cage 5 are not in contact. Since the relationship between the distance W from the edge and the diameter Db of the ball 4 is set to Db> W, the drop of the ball 4 from the pocket 5a of the cage 5 is prevented.
  • FIG. 5 is a diagram showing the range in which the ball 4 is disengaged from the track groove 7 of the outer joint member 2 at the maximum operating angle, as shown in FIG. 1b.
  • FIG. 5 shows a range in which the ball 4 is detached from the track groove 7 of the outer joint member 2 with an arrow.
  • the fixed type constant velocity universal joint 1 of the present embodiment has a maximum operating angle of 50 °, a phase angle ⁇ 0 and a phase angle ⁇ 1 of 20 ° centered on the phase angle ⁇ 0, and a phase angle ⁇ 0.
  • the phase angle ⁇ 2 is 20 °
  • the range in which the ball 4 is removed from the track groove 7 of the outer joint member 2 is 40 °.
  • One ball 4 positioned at the phase angle ⁇ 0 in FIGS. 3a and 3b is taken as an example with respect to the range where the ball 4 is removed from the track groove 7, that is, the phase angle range where the ball 4 and the track groove 7 are in a non-contact state
  • the axis No-No of the outer joint member 2 and the axis Ni-Ni of the inner joint member 3 (intermediate shaft 14) are kept constant, and the fixed type constant velocity universal joint 1 is counterclockwise from the phase angle ⁇ 0.
  • a non-contact state with the track groove 7 is started.
  • the specific single ball 4 has been described as an example. However, when the fixed type constant velocity universal joint 1 is rotated, the eight balls 4 are actually in a non-contact state sequentially. Will pass the range.
  • FIG. 6 shows the analysis result of the phase angle and the track load at the maximum operating angle for one ball 4 of the above-described model by a bold line.
  • FIG. 6 hatched portions as a range of phase angles in which the balls 4 and the track grooves 7 of the outer joint member 2 are in a non-contact state are displayed in an overlapping manner.
  • the relationship between the phase angle and the track load in the fixed type constant velocity universal joint 1 of the present embodiment was considered as follows.
  • the track load immediately after returning to the end of the track groove 7 of the outer joint member 2 at the phase angle ⁇ 1 is in contact with the track grooves 7 because all the eight balls 4 are in contact with each other.
  • the track load at ⁇ 1 of the analysis result can be regarded as the track load at ⁇ 1 of the fixed type constant velocity universal joint 1 of the present embodiment.
  • the track load P1 at which the ball 4 returns to the opening-side end of the track groove 7 of the outer joint member 2 at the phase angle ⁇ 1 and starts to contact the track groove 7 is the phase load ⁇ 1 of the outer joint member 2 at the phase angle ⁇ 2. It has been found that the load is significantly larger than the track load P2 that starts off from the end of the track groove 7 on the opening side and starts a non-contact state with the track groove 7.
  • the ball 4 returns to the end of the outer joint member 2 on the opening side of the track groove 7 at the phase angle ⁇ 1 and starts contact with the track groove 7.
  • the contact points C1, C3 between the ball 4 and the track grooves 7, 9 pass through the center Ob of the ball 4 and the joint center O as shown in FIG.
  • a track load inclined in a counterclockwise direction with a contact angle ⁇ with respect to a straight line acts, a distribution or balance of the track load changes due to a non-contact state, a large track load P1, P2, etc.
  • the characteristic configuration (2) of the fixed type constant velocity universal joint 1 of the present embodiment is that the column portions on both sides of the pocket 5a of the cage 5 that accommodates the ball 4 at the phase angle ⁇ 1 in a state where the maximum operating angle is taken. 5b, 5b ′, the end portion 6a on the opening side of the spherical inner peripheral surface 6 of the outer joint member 2 faces the spherical outer peripheral surface 12 of the cage 5 in the column portion 5b on the side where the phase angle is larger than the phase angle ⁇ 1.
  • the projection end Eo see FIG.
  • FIG. 8a is a right side view showing the state where the ball returns to the track groove of the outer joint member at the maximum operating angle, and the axis of the inner joint member is displayed in a horizontal state
  • FIG. 8b shows the axis of the outer joint member
  • FIG. 8 c is a right side view displayed in a horizontal state
  • FIG. 8 c is a right side view displayed with the cage axis line in a horizontal state
  • FIG. 9 shows a longitudinal section of a fixed type constant velocity universal joint at the groove bottom of the track groove at a phase angle ⁇ 1 at which the ball returns to the track groove of the outer joint member, and shows the inner joint as viewed along the line AA in FIG.
  • FIG. 10 shows a vertical cross section of a fixed type constant velocity universal joint at the center in the circumferential direction of the pillar portion 5b of the cage on the side where the phase angle is larger than the phase angle ⁇ 1 at which the ball returns to the track groove of the outer joint member.
  • the ball 4 when the maximum operating angle is taken, the ball 4 returns to the track groove 7 of the outer joint member 2 at the phase angle ⁇ 1 and starts contact with the track groove 7 To do. At this time, it contacts the edge of the entrance chamfer 20 of the contact point locus CLo in FIG. As described above, the track load P1 of the ball 4 is significantly larger than the track load P2 that starts to be out of contact with the track groove 7 at the phase angle ⁇ 2 from the end of the outer joint member 2 on the opening side of the track groove 7. Big.
  • the pillar 5 b of the cage on the side where the phase angle is larger than the phase angle ⁇ 1 at which the ball returns to the track groove of the outer joint member is the spherical shape of the outer joint member 2.
  • a large spherical force is applied to the column portion from both ends of the inner peripheral surface 6 between the end portion 6a on the opening side of the inner peripheral surface 6 and the end portion 8a on the inner side of the spherical outer peripheral surface 8 of the inner joint member 3.
  • an end 6a on the opening side of the spherical inner peripheral surface 6 of the outer joint member 2 and an end 8a on the back side of the spherical outer peripheral surface 8 of the inner joint member 3 are shown.
  • the column portion 5b is not in a sheared state with respect to the spherical force.
  • FIGS. 11a is a front view of the fixed type constant velocity universal joint when the torque transmission ball returns to the track groove of the outer joint member
  • FIG. 11b is a right side view of FIG. 11a
  • FIG. 12 is a diagram showing the relationship among the spherical inner peripheral surface of the outer joint member, the spherical outer peripheral surface of the inner joint member, and the cage as viewed in the direction G in FIG. 11b.
  • FIG. 11a and 11b show the axis of the cage 5 arranged in the horizontal direction.
  • FIG. 11b corresponds to FIG. 8c described above.
  • the spherical inner peripheral surface 6 of the outer joint member 2 is indicated by a broken line
  • the spherical outer peripheral surface 8 of the inner joint member 3 is indicated by a solid line.
  • the outline on the spherical outer peripheral surface 12 side is indicated by a solid line
  • the outline on the spherical inner peripheral surface 13 side is indicated by a broken line.
  • the projected end portion obtained by projecting the end portion 6 a on the opening side of the spherical inner peripheral surface 6 of the outer joint member 2 toward the spherical outer peripheral surface 12 of the cage 5 in the vertical direction is Eo.
  • a projected end portion obtained by projecting the end portion 8a on the back side of the spherical outer peripheral surface 8 of the inner joint member 3 toward the spherical inner peripheral surface 13 of the cage 5 in the vertical direction is Ei.
  • the projection end Eo and the projection end Ei overlap at least partially in the axial direction of the cage 5.
  • the projection end Eo and the projection end Ei overlap in a triangular shape, and the triangular overlap portion T has a length Lt in the axial direction of the cage 5.
  • a projected end (Eo) obtained by projecting an end of the spherical inner peripheral surface of the outer joint member on the opening side in a vertical direction toward the spherical outer peripheral surface of the cage, and a spherical shape of the inner joint member The projected end portion (Ei) obtained by projecting the end on the back side of the outer peripheral surface in the vertical direction toward the spherical inner peripheral surface of the cage overlaps at least partially in the axial direction of the cage.
  • the length Lt of the overlapping portion in the axial direction of the cage has the above meaning.
  • a projected end Ei obtained by projecting the end 8a on the inner side of the spherical outer peripheral surface 8 of the inner joint member 3 in the vertical direction toward the spherical inner peripheral surface 13 of the cage 5, in the axial direction of the cage 5.
  • the column portion 5b Since the projection end Eo and the projection end Ei overlap at least partly in the axial direction of the cage 5, the column portion 5b does not enter a sheared state with respect to the spherical force. Therefore, the strength of the cage 5 can be ensured and an increase in weight can be suppressed.
  • the setting range of the overlapping portion T between the projection end Eo and the projection end Ei will be described.
  • the radius of the spherical outer circumferential surface 12 of the cage 5 Ro
  • the radius of the spherical inner circumferential surface 13 is Ri
  • the radius of the center of the radial thickness of the cage 5 is Rm
  • Rm ( Ro + Ri) / 2.
  • the ratio Lt / Rm between the length Lt of the overlapping portion T in the axial direction of the cage 5 and the radius of the center of the radial thickness of the cage 5 to Rm is preferably set to 0.03 or more.
  • the ratio Lt / Rm is less than 0.03
  • the surface pressure of the overlapping portion T becomes high, and the shear state of the column portion 5b cannot be sufficiently suppressed.
  • FIGS. 13a is a longitudinal sectional view of a fixed type constant velocity universal joint according to the present embodiment
  • FIG. 13b is a right side view of FIG. 13a
  • 14a is a longitudinal sectional view of the outer joint member of FIG. 13a
  • FIG. 14b is a right side view of FIG. 14a
  • 15a is a front view of the inner joint member of FIG. 13a
  • FIG. 15b is a right side view of FIG. 15a.
  • the fixed type constant velocity universal joint 1 mainly includes an outer joint member 2, an inner joint member 3, a ball 4 and a cage 5.
  • Eight track grooves 7 are formed on the spherical inner peripheral surface 6 of the outer joint member 2, and eight track grooves facing the track grooves 7 of the outer joint member 2 are formed on the spherical outer peripheral surface 8 of the inner joint member 3. 9 is formed.
  • a cage 5 for holding the ball 4 is disposed between the spherical inner peripheral surface 6 of the outer joint member 2 and the spherical outer peripheral surface 8 of the inner joint member 3.
  • the spherical outer peripheral surface 12 of the cage 5 is slidably fitted to the spherical inner peripheral surface 6 of the outer joint member 2, and the spherical inner peripheral surface 13 of the cage 5 slides on the spherical outer peripheral surface 8 of the inner joint member 3. Fits freely.
  • the centers of curvature of the spherical inner peripheral surface 6 of the outer joint member 2 and the spherical outer peripheral surface 8 of the inner joint member 3 are respectively formed at the joint center O, and the spherical inner peripheral surface 6 of the outer joint member 2 and the spherical surface of the inner joint member 3 are formed.
  • the centers of curvature of the spherical outer peripheral surface 12 and the spherical inner peripheral surface 13 of the cage 5 that are respectively fitted to the outer peripheral surface 8 are also located at the joint center O.
  • the eight track grooves 7, 9 of the outer joint member 2 and the inner joint member 3, respectively, are circumferential with respect to the joint axis NN.
  • the track grooves 7 ⁇ / b> A, 7 ⁇ / b> B and 9 ⁇ / b> A, 9 ⁇ / b> B are formed in directions opposite to each other.
  • eight balls 4 are arranged at the intersections of the track grooves 7A, 9A and 7B, 9B which form a pair of the outer joint member 2 and the inner joint member 3.
  • FIG. 13a the track grooves 7 and 9 are shown in a state in which the cross sections in the plane M shown in FIG.
  • the joint axis NN is also the axis No-No of the outer joint member and the axis Ni-Ni of the inner joint member.
  • the track groove 7 of the outer joint member 2 has a ball track center line X
  • the track groove 7 has a first ball track center line Xa having an arc-shaped ball track center line Xa with the joint center O as the center of curvature.
  • Track groove portion 7a and a second track groove portion 7b having a linear ball track center line Xb.
  • the ball track center line Xa of the second track groove portion 7b is aligned with the ball track center line Xa of the first track groove portion 7a.
  • Xb is smoothly connected as a tangent.
  • the track groove 9 of the inner joint member 3 has a ball track center line Y, and the track groove 9 has a first arc-shaped ball track center line Ya with the joint center O as the center of curvature.
  • Track groove portion 9a and a second track groove portion 9b having a linear ball track center line Yb, and the ball track center line of the second track groove portion 9b is aligned with the ball track center line Ya of the first track groove portion 9a.
  • Yb is smoothly connected as a tangent.
  • the track grooves 7 of the outer joint member 2 are given the reference numerals of the track grooves 7A and 7B due to the difference in the inclination direction.
  • the plane M including the ball track center line X and the joint center O of the track groove 7A is inclined by an angle ⁇ with respect to the joint axis NN.
  • the track groove 7B adjacent to the track groove 7A in the circumferential direction is not shown, but the plane M including the ball track center line X and the joint center O of the track groove 7B is in relation to the joint axis NN.
  • the track groove 7A is inclined by an angle ⁇ in the opposite direction to the inclination direction of the track groove 7A.
  • the entire area of the ball track center line X of the track groove 7A that is, both the ball track center line Xa of the first track groove portion 7a and the ball track center line Xb of the second track groove portion 7b are on the plane M. Is formed.
  • the present invention is not limited to this, and a mode in which only the ball trajectory center line Xa of the first track groove portion 7a is included in the plane M can also be implemented. Therefore, at least the first track groove portion 7a in which the plane M including the ball track center line Xa and the joint center O of the first track groove portion 7a is inclined with respect to the joint axis NN and the inclination direction is adjacent in the circumferential direction. 7a may be formed in opposite directions.
  • the track groove codes are supplemented.
  • reference numeral 7 is attached, and the first track groove part is assigned 7a, and the second track groove part is given 7b.
  • reference numerals 7A and 7B are attached, and reference numerals 7Aa and 7Ba are attached to the first track groove parts, and reference signs 7Ab and 7Bb are attached to the second track groove parts.
  • the track grooves of the inner joint member 3 to be described later are also given the same reference numerals.
  • the track grooves 9 of the inner joint member 3 are denoted by the reference numerals of the track grooves 9A and 9B because of the difference in inclination direction.
  • the plane Q including the ball track center line Y and the joint center O of the track groove 9A is inclined by an angle ⁇ with respect to the joint axis NN.
  • the track groove 9B adjacent to the track groove 9A in the circumferential direction is not shown, but the plane Q including the ball track center line Y and the joint center O of the track groove 9B is in relation to the joint axis NN.
  • the track groove 9A is inclined by an angle ⁇ in the direction opposite to the inclination direction of the track groove 9A.
  • the inclination angle ⁇ is preferably set to 4 ° to 12 ° in consideration of the operability of the constant velocity universal joint 1 and the spherical surface width I on the closest side of the track groove of the inner joint member 3.
  • the entire region of the ball track center line Y of the track groove 9A that is, the ball track center line Ya of the first track groove portion 9a and the balls of the second track groove portion 9b. Both of the track center lines Yb are formed on the plane Q.
  • the present invention is not limited to this, and a mode in which only the ball trajectory center line Ya of the first track groove portion 9a is included in the plane Q can also be implemented. Therefore, a plane Q including at least the ball track center line Ya of the first track groove 9a and the joint center O is inclined in the circumferential direction with respect to the joint axis NN, and the inclined direction is adjacent to the circumferential direction in the first direction.
  • the track grooves 9a may be formed in opposite directions.
  • the ball trajectory center line Y of the track groove 9 of the inner joint member 3 is based on the plane P including the joint center O at the operating angle of 0 ° as a reference, and the ball trajectory center line of the track groove 7 that forms a pair of the outer joint member 2 X and mirror image symmetry.
  • FIG. 13a details of the track grooves as seen from the longitudinal cross sections of the outer joint member 2 and the inner joint member 3 will be described.
  • 14a is a cross-sectional view of the track groove 7A of the outer joint member 2 of FIG. 14a as viewed on a plane M including the ball track center line X and the joint center O. Therefore, strictly speaking, it is not a longitudinal sectional view in a plane including the joint axis NN, but shows a section inclined by an angle ⁇ .
  • FIG. 13a shows the track groove 7A of the outer joint member 2, but the track groove 7B is the same as the track groove 7A except for the inclination direction opposite to the track groove 7A. Since there is, explanation is omitted.
  • a track groove 7A is formed on the spherical inner peripheral surface 6 of the outer joint member 2 substantially along the axial direction.
  • the track groove 7A has a ball track center line X
  • the track groove 7A has a first track groove portion 7Aa having an arc-shaped ball track center line Xa with the joint center O as the center of curvature (no axial offset).
  • a second track groove portion 7Ab having a linear ball trajectory center line Xb. Then, at the end J on the opening side of the ball track center line Xa of the first track groove portion 7Aa, the linear ball track center line Xb of the second track groove portion 7Ab is smoothly connected as a tangent line. That is, the end portion J is a connection point between the first track groove portion 7Aa and the second track groove 7Ab.
  • the ball trajectory center line Xb is formed so as to approach the joint axis NN as it goes to the opening side. Thereby, it can suppress that a wedge angle becomes excessive.
  • FIG. 15B is a cross-sectional view of the track groove 9A of the inner joint member 3 of FIG. Therefore, strictly speaking, it is not a longitudinal sectional view in a plane including the joint axis NN, but shows a section inclined by an angle ⁇ .
  • FIG. 13a shows the track groove 9A of the inner joint member 3
  • the track groove 9B is the same as the track groove 9A except for the inclination direction opposite to the track groove 9A. Since there is, explanation is omitted.
  • a track groove 9A is formed in the spherical outer peripheral surface 8 of the inner joint member 3 substantially along the axial direction.
  • the track groove 9A has a ball track center line Y, and the track groove 9A has a first track groove portion 9Aa having an arc-shaped ball track center line Ya with the joint center O as the center of curvature (no axial offset). And a second track groove portion 9Ab having a linear ball trajectory center line Yb.
  • the ball track center line Yb of the second track groove portion 9Ab is smoothly connected as a tangent at the end J 'on the back side of the ball track center line Ya of the first track groove portion 9Aa. That is, the end J ′ is a connection point between the first track groove 9Aa and the second track groove 9Ab.
  • the second track groove portion 9Ab connected as a tangent at the end portion J ′ on the back side of the ball track center line Ya of the first track groove portion 9Aa.
  • the straight ball trajectory center line Yb is formed so as to approach the joint axis NN toward the back side. Thereby, it can suppress that a wedge angle becomes excessive.
  • a straight line connecting the end portion J 'and the joint center O is defined as S'.
  • the joint axis N′-N ′ projected on the plane Q including the ball track center line Y and the joint center O of the track groove 9A is inclined by ⁇ with respect to the joint axis NN, and the axis N′-N ′.
  • An angle formed by the perpendicular K and the straight line S ′ at the joint center O is ⁇ ′.
  • the angle ⁇ formed with respect to the plane P including the joint center O in which the straight lines S and S ′ are at an operating angle of 0 ° will be described.
  • the ball 4 moves by ⁇ / 2 with respect to the plane P including the joint center O of the outer joint member 2 and the inner joint member 3.
  • the angle ⁇ is determined from 1 ⁇ 2 of the frequently used operating angle, and the range of the track groove with which the ball 4 contacts is determined within the frequently used operating angle range.
  • the operating angle that is frequently used is defined.
  • the common angle of the joint refers to the operating angle generated in the fixed constant velocity universal joint of the front drive shaft when the vehicle is traveling straight on a horizontal and flat road surface when the vehicle is in a straight traveling state.
  • the service angle is usually selected and determined between 2 ° and 15 ° according to the design conditions for each vehicle type. *
  • the end J of the ball track center line Xa of the first track groove 7Aa becomes the center position of the ball when moved to the most opening side along the axial direction at the normal angle.
  • the end portion J ′ of the ball track center line Ya of the first track groove portion 9Aa is the center position of the ball when moved to the farthest side along the axial direction at the normal angle. . Since it is set in this way, in the range of the normal angle, the ball 4 is located in the first track groove portions 7Aa and 9Aa of the outer joint member 2 and the inner joint member 3 and 7Ba and 9Ba whose inclination directions are opposite to each other.
  • the clearance between the pocket portion 5a of the cage 5 and the ball 4 may be set as a clearance.
  • the clearance is preferably set to about 0 to 40 ⁇ m.
  • the balls 4 arranged in the circumferential direction are temporarily separated and positioned in the first track groove portions 7Aa and 9Aa and the second track groove portions 7Ab and 9Ab.
  • the forces acting from the balls 4 on the pockets 5a of the cage 5 are not balanced, and the spherical contact portions 12 and 6 between the cage 5 and the outer joint member 2 and the cage 5 and the inner joint member 3
  • the contact force of the spherical contact portions 13 and 8 is generated, the constant velocity universal joint 1 of the present embodiment can suppress torque loss and heat generation comprehensively because the frequency of use is low in the high operating angle range. Therefore, a highly efficient fixed type constant velocity universal joint with less torque loss and heat generation can be realized.
  • the overall configuration of the fixed type constant velocity universal joint 1 of the present embodiment is as described above.
  • the fixed type constant velocity universal joint 1 of the present embodiment is set to a maximum operating angle that greatly exceeds 50 °, but the characteristic configuration is as follows, as in the first embodiment. (1) When the maximum operating angle is taken, the ball 4 that moves most toward the opening side of the track groove 7 of the outer joint member 2 is the end on the opening side of the track groove 7 of the outer joint member 2 at the phase angle ⁇ 2. And an operation mode in which the contact state with the track groove 7 is started at the phase angle ⁇ 1 and returned to the end portion of the outer joint member 2 on the opening side of the track groove 7 at the phase angle ⁇ 1. Having.
  • FIG. 2 of the fixed type constant velocity universal joint 1 according to the first embodiment and the description based on FIGS. 3 to 12 regarding the above-described characteristic configuration and its effects are as follows. Since the same applies to the quick universal joint 1, the contents described in the first embodiment will be applied mutatis mutandis and only the main points will be described.
  • the length L1 from the joint center O to the opening side end of the outer joint member 2 of the fixed type constant velocity universal joint 1 of the present embodiment shown in FIG. 13a is greatly shortened, and the above characteristic configuration ( It becomes the operation mode of 1).
  • the radius of the spherical outer circumferential surface 12 of the cage 5 shown in FIG. 13a is Ro
  • the radius of the spherical inner circumferential surface 13 is Ri
  • Projection end Eo in which the end of the spherical inner peripheral surface of the outer joint member is projected in the vertical direction toward the spherical outer peripheral surface of the cage, and the spherical outer periphery of the inner joint member in the column portion on the side having the larger corner
  • the ratio Lt / Rm of the center radius of the wall thickness to Rm is 0.03 or more Is set to
  • the track grooves 7 and 9 are inclined in the circumferential direction. Therefore, when rotated in the counterclockwise direction shown in FIG.
  • the phase angle ⁇ 1 that returns to the end of the track groove 7 on the opening side and starts contact with the track groove 7 is, for example, 24 ° for the track groove 7A and 27 ° for the track groove 7B.
  • the phase angle ⁇ 2 at which the outer joint member 2 starts off from the end of the track groove 7 on the opening side and starts a non-contact state with the track groove 7 is, for example, 336 ° in the track groove 7A, and in the track groove 7B, for example, 333 °. That is, when rotated counterclockwise as shown in FIG.
  • the maximum operating angle which is the characteristic configuration (2) of the fixed type constant velocity universal joint 1 of the present embodiment, is taken, and the phase angle ⁇ 1 Of the column portions 5b and 5b 'on both sides of the pocket 5a of the cage 5 that accommodates the ball 4, the opening of the spherical inner peripheral surface 6 of the outer joint member 2 in the column portion 5b on the side where the phase angle is larger than the phase angle ⁇ 1.
  • the projecting end Eo in which the end 6a on the side is projected in the vertical direction toward the spherical outer peripheral surface 12 of the cage 5 and the end 8a on the inner side of the spherical outer peripheral surface 8 of the inner joint member 3 are spherical.
  • the projection end Ei projected in the vertical direction toward the inner peripheral surface 13 overlaps at least partially in the axial direction of the cage 5 in the spherical inner peripheral surface 6 on both sides of the track groove 7B. Is the spherical inner peripheral surface 6 on the side of the travel, and the inner side facing this spherical inner peripheral surface 6 The spherical outer peripheral surface 8 of the joint member 3 is formed. This is because the track groove 7B has a shorter contact point locus than the track groove 7A when rotated counterclockwise.
  • FIGS. 16a and 16b A fixed type constant velocity universal joint according to a third embodiment of the present invention will be described with reference to FIGS. 16a and 16b.
  • 16a is a longitudinal sectional view of a fixed type constant velocity universal joint according to the present embodiment
  • FIG. 16b is a right side view of FIG. 16a.
  • the fixed type constant velocity universal joint 1 of the present embodiment is based on an undercut free type constant velocity universal joint, and includes an outer joint member 2, an inner joint member 3, a torque transmission ball (also simply referred to as a ball) 4, and
  • the cage 5 has a main configuration.
  • Six track grooves 7 are formed on the spherical inner peripheral surface 6 of the outer joint member 2 at equal intervals in the circumferential direction and along the axial direction.
  • Track grooves 9 facing the track grooves 7 of the outer joint member 2 are formed on the spherical outer peripheral surface 8 of the inner joint member 3 at equal intervals in the circumferential direction and along the axial direction.
  • Six balls 4 for transmitting torque are incorporated one by one between the track groove 7 of the outer joint member 2 and the track groove 9 of the inner joint member 3.
  • a cage 5 that holds the ball 4 is disposed between the spherical inner peripheral surface 6 of the outer joint member 2 and the spherical outer peripheral surface 8 of the inner joint member 3. The ball 4 is accommodated in the pocket 5 a of the cage 5.
  • the spherical outer peripheral surface 12 of the cage 5 is slidably fitted to the spherical inner peripheral surface 6 of the outer joint member 2, and the spherical inner peripheral surface 13 of the cage 5 slides on the spherical outer peripheral surface 8 of the inner joint member 3. Fits freely.
  • the curvature center O3 of the spherical inner circumferential surface 6 of the outer joint member 2 and the spherical outer circumferential surface 12 of the cage 5, and the curvature center O4 of the spherical outer circumferential surface 8 of the inner joint member 3 and the spherical inner circumferential surface 13 of the cage 5 are:
  • a small amount f2 is offset at equal distances on the opposite side in the axial direction with respect to the joint center O.
  • the curved track groove 7 of the outer joint member 2 includes a curved track groove portion 7 a located on the back side of the outer joint member 2 and a linear track groove portion 7 s located on the opening side.
  • the groove 9 is composed of a curved track groove portion 9a located on the opening side and a linear track groove portion 9s located on the back side.
  • the center of curvature O1 ′ of the ball track center line Xa of the curved track groove portion 7a of the outer joint member 2 and the center of curvature O2 ′ of the ball track center line Ya of the curved track groove portion 9a of the inner joint member 3 are located at the joint center O. On the other hand, it is offset at an equal distance f1 on the opposite side in the axial direction.
  • the ball track center line Xa of the curved track groove portion 7a of the outer joint member 2 and the ball track center line Xs of the linear track groove 7s are tangentially connected, and the ball track center line Xs of the linear track groove portion 7s is the center of curvature. It is formed in parallel with the joint axis NN from the axial position of O1 ′ to the opening side.
  • the ball track center line Ya of the curved track groove portion 9a of the inner joint member 3 and the ball track center line Ys of the linear track groove 9s are tangentially connected, and the ball track center line Ys of the linear track groove portion 9s is the center of curvature. It is formed in parallel with the joint axis NN from the axial position of O2 ′ to the back side.
  • the overall configuration of the fixed type constant velocity universal joint 1 of the present embodiment is as described above.
  • the fixed type constant velocity universal joint 1 of this embodiment is set to the maximum operating angle exceeding 50 degrees
  • the characteristic structure is as follows similarly to 1st Embodiment. (1)
  • the ball 4 that moves most toward the opening side of the track groove 7 of the outer joint member 2 is the end on the opening side of the track groove 7 of the outer joint member 2 at the phase angle ⁇ 2.
  • an operation mode in which the contact state with the track groove 7 is started at the phase angle ⁇ 1 and returned to the end portion of the outer joint member 2 on the opening side of the track groove 7 at the phase angle ⁇ 1.
  • FIG. 2 of the fixed type constant velocity universal joint 1 according to the first embodiment and the description based on FIGS. 3 to 12 regarding the above-described characteristic configuration and its effects are as follows. Since the same applies to the quick universal joint 1, the contents described in the first embodiment will be applied mutatis mutandis and only the main points will be described.
  • the length L1 from the joint center O to the opening side end of the outer joint member 2 of the fixed type constant velocity universal joint 1 of the present embodiment shown in FIG. 13a is greatly shortened, and the above characteristic configuration ( It becomes the operation mode of 1).
  • the radius of the spherical outer peripheral surface 12 of the cage 5 shown in FIG. 16a is Ro
  • the radius of the spherical inner circumferential surface 13 is Ri
  • Projection end Eo in which the end of the spherical inner peripheral surface of the outer joint member is projected in the vertical direction toward the spherical outer peripheral surface of the cage, and the spherical outer periphery of the inner joint member in the column portion on the side having the larger corner
  • the ratio Lt / Rm of the center radius of the wall thickness to Rm is 0.03 or more Is set to
  • the phase angle ⁇ 1 that returns to the opening end of the track groove 7 of the outer joint member 2 and starts the contact state with the track groove 7 is 30 °.
  • the phase angle ⁇ 2 at which the member deviates from the end of the track groove 7 on the opening side and starts a non-contact state with the track groove 7 is 330 °.
  • the fixed type constant velocity universal joint 1 of each embodiment described above has the following characteristic configurations (1) and (2), the strength of the cage 5 can be obtained even when the maximum operating angle is larger than the conventional one. Can be secured, and an increase in weight can be suppressed.
  • (1) When the maximum operating angle is taken, the ball 4 that moves most toward the opening side of the track groove 7 of the outer joint member 2 is the end on the opening side of the track groove 7 of the outer joint member 2 at the phase angle ⁇ 2. And an operation mode in which the contact state with the track groove 7 is started at the phase angle ⁇ 1 and returned to the end portion of the outer joint member 2 on the opening side of the track groove 7 at the phase angle ⁇ 1.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
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  • Bearings For Parts Moving Linearly (AREA)
  • Pivots And Pivotal Connections (AREA)

Abstract

L'invention concerne un joint homocinétique de type fixe (1) comprenant : un élément de joint externe (2) dans lequel plusieurs rainures de guidage (7) s'étendant principalement de manière longitudinale sont formées dans une surface périphérique interne sphérique (6) et ledit élément de joint externe comporte un côté ouvert et un côté intérieur séparés dans une direction axiale ; un élément de joint interne (3) dans lequel plusieurs rainures de guidage (9) s'étendant principalement de manière longitudinale sont formées pour correspondre aux rainures de guidage (7) de l'élément de joint externe (2) dans une surface périphérique externe sphérique (8) ; des billes de transmission de couple (4) incorporées entre les rainures de guidage opposées (7, 9) ; et un dispositif de retenue (5) qui retient les billes de transmission de couple (4) et sur lequel sont formées une surface périphérique externe sphérique (12) guidée sur la surface périphérique interne sphérique (6) de l'élément de joint externe (2) et une surface périphérique interne sphérique (13) guidée sur la surface périphérique externe sphérique (8) de l'élément de joint interne (3) ; le joint homocinétique de type fixe (1) est caractérisé en ce que : lorsqu'un angle de fonctionnement maximal est adopté, les billes de transmission de couple (4) qui se sont déplacées le plus loin vers le côté ouvert des rainures de guidage (7) de l'élément de joint externe (2) ont un mode de fonctionnement dans lequel dans un angle de phase φ2, les billes quittent les parties terminales côté ouvert des rainures de guidage (7) de l'élément de joint externe (2) pour commencer un état sans contact avec les rainures de guidage (7), et dans un angle de phase φ1, les billes retournent vers les parties terminales côté ouvert des rainures de guidage (7) de l'élément de joint externe (2) pour commencer un état de contact avec les rainures de guidage (7) ; et dans un état dans lequel l'angle de fonctionnement maximal a été adopté, parmi les parties de colonne (5b, 5b') au niveau des deux côtés d'une cavité (5a) du dispositif de retenue (5) logeant les billes de transmission de couple dans l'angle de phase φ1, dans la partie de colonne (5b) au niveau du côté où l'angle de phase est supérieur à l'angle de phase φ1, une partie terminale saillante (Eo), qui est une saillie perpendiculaire de la partie terminale côté ouvert de la surface périphérique interne sphérique (6) de l'élément de joint externe (2) faisant saillie vers la surface périphérique externe sphérique (12) du dispositif de retenue (5), et une partie terminale saillante (Ei), qui est une saillie perpendiculaire de la partie terminale côté intérieur de la surface périphérique externe sphérique (8) de l'élément de joint interne (3) faisant saillie vers la surface périphérique interne sphérique (13) du dispositif de retenue (5), se chevauchent dans au moins une partie du dispositif de retenue (5) dans la direction axiale.
PCT/JP2019/013212 2018-04-03 2019-03-27 Joint homocinétique de type fixe WO2019194046A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
DE112019001761.6T DE112019001761T5 (de) 2018-04-03 2019-03-27 Universales Gleichlauffestgelenk
CN201980022715.8A CN111919044B (zh) 2018-04-03 2019-03-27 固定式等速万向联轴器
US17/041,206 US11927226B2 (en) 2018-04-03 2019-03-27 Fixed type constant velocity universal joint

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP2018071601 2018-04-03
JP2018-071601 2018-04-03
JP2019-048306 2019-03-15
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JPS61228125A (ja) * 1985-04-03 1986-10-11 Nippon Seiko Kk 等速ジヨイント
JP2004251326A (ja) * 2003-02-18 2004-09-09 Ntn Corp 固定型等速自在継手
JP2007100806A (ja) * 2005-10-03 2007-04-19 Ntn Corp 固定式等速自在継手
WO2008018290A1 (fr) * 2006-08-07 2008-02-14 Ntn Corporation Joint universel à vitesse constante fixe
JP2008089149A (ja) * 2006-10-04 2008-04-17 Ntn Corp 固定式等速自在継手
JP2008106881A (ja) * 2006-10-26 2008-05-08 Ntn Corp 固定式等速自在継手
JP2009522508A (ja) * 2005-12-29 2009-06-11 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 大きな屈曲角の固定式等速自在継手

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS61228125A (ja) * 1985-04-03 1986-10-11 Nippon Seiko Kk 等速ジヨイント
JP2004251326A (ja) * 2003-02-18 2004-09-09 Ntn Corp 固定型等速自在継手
JP2007100806A (ja) * 2005-10-03 2007-04-19 Ntn Corp 固定式等速自在継手
JP2009522508A (ja) * 2005-12-29 2009-06-11 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 大きな屈曲角の固定式等速自在継手
WO2008018290A1 (fr) * 2006-08-07 2008-02-14 Ntn Corporation Joint universel à vitesse constante fixe
JP2008089149A (ja) * 2006-10-04 2008-04-17 Ntn Corp 固定式等速自在継手
JP2008106881A (ja) * 2006-10-26 2008-05-08 Ntn Corp 固定式等速自在継手

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