JP2008256022A - Constant velocity universal joint - Google Patents

Constant velocity universal joint Download PDF

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Publication number
JP2008256022A
JP2008256022A JP2007096558A JP2007096558A JP2008256022A JP 2008256022 A JP2008256022 A JP 2008256022A JP 2007096558 A JP2007096558 A JP 2007096558A JP 2007096558 A JP2007096558 A JP 2007096558A JP 2008256022 A JP2008256022 A JP 2008256022A
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Japan
Prior art keywords
joint
convex
shaft
constant velocity
velocity universal
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JP2007096558A
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Japanese (ja)
Inventor
Yuichi Asano
Akira Nakagawa
亮 中川
祐一 淺野
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Ntn Corp
Ntn株式会社
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Priority to JP2007096558A priority Critical patent/JP2008256022A/en
Priority claimed from CN 200880001344 external-priority patent/CN101611233B/en
Priority claimed from US12/522,289 external-priority patent/US8506202B2/en
Publication of JP2008256022A publication Critical patent/JP2008256022A/en
Pending legal-status Critical Current

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Abstract

<P>PROBLEM TO BE SOLVED: To provide a constant velocity universal joint having a recessed and projecting fitting structure reduced in costs by simplifying the manufacture of an outer joint member or an inner joint member, and besides hardly causing backlash in a shaft connection portion and firmly connecting the inner joint member to a shaft. <P>SOLUTION: At least one of the track groove 9 of the outer joint member and the track groove 11 of the inner joint member is formed by cold forging finish. A component element formed of the outer joint member, the inner joint member, a ball 3 and a cage 4 is assembled at random. The inner joint member and the shaft 5 inserted into the shaft hole of the inner joint member are coupled to each other through the recessed and projecting fitting structure M. The entire area of a fitting/contact portion 38 between the projecting portion 35 of one of the inner joint member and the shaft 5 and the recessed portion 36 of a counter-member fitted to the projecting portion 35 is tightly stuck. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention is used in, for example, a power transmission system of an automobile or various industrial machines. If the fixed constant velocity universal joint that allows only angular displacement between two axes of the driving side and the driven side or only angular displacement is used. The present invention relates to a sliding type constant velocity universal joint that allows axial displacement, a drive shaft using these, and a bearing unit for a drive wheel.
  For power transmission systems of automobiles and various industrial machines, such as front wheel drive vehicles and independent suspension type rear wheel drive vehicles, only angular displacement is used as a means to transmit the rotational force from the engine of the vehicle to the wheels at a constant speed. There are used fixed type constant velocity universal joints that allow and sliding type constant velocity universal joints that allow both angular displacement and axial displacement.
  Examples of the drive shaft include a propeller shaft that transmits a rotational drive force from a transmission to a differential, and a drive shaft that transmits a rotational drive force from a differential to a wheel. In addition, the Barfield type constant velocity universal joint (BJ) is well known as the fixed type constant velocity universal joint, and the double offset type constant velocity universal joint (DOJ) is widely used as the sliding type constant velocity universal joint. Are known.
  For example, a fixed type constant velocity universal joint of BJ type is formed by pairing an outer joint member in which a plurality of track grooves extending in the axial direction are formed on a spherical inner peripheral surface and a track groove of the outer joint member in the axial direction. An inner joint member having a track groove extending on the outer peripheral surface of the spherical surface, a plurality of balls transmitting torque between the track groove of the outer joint member and the track groove of the inner joint member, and the outer joint member And a cage for holding the ball interposed between the spherical inner peripheral surface and the spherical outer peripheral surface of the inner joint member.
  The DOJ-type sliding constant velocity universal joint is paired with an outer joint member in which a plurality of linear track grooves extending in the axial direction are formed on a cylindrical inner peripheral surface, and a track groove of the outer joint member. A plurality of balls that transmit torque by being interposed between the track groove of the outer joint member and the track groove of the inner joint member. And a cage for holding the ball interposed between the cylindrical inner peripheral surface of the outer joint member and the spherical outer peripheral surface of the inner joint member.
  The outer joint member and the inner joint member in the fixed type constant velocity universal joint or the sliding type constant velocity universal joint are generally manufactured in the following manner. First, a cylindrical billet is formed into a schematic shape of an outer joint member or an inner joint member by hot forging, warm forging or cold forging, and the outer peripheral surface, inner peripheral surface and end surface of this material are turned. After that, heat treatment is performed, and the inner peripheral surface and the track groove are finished by grinding or quenching steel cutting.
For the outer joint member and inner joint member manufactured in this way, the PCD clearance and the like are within the specified range when the inner part including the ball and cage is incorporated into the inner joint member. To combine them selectively. That is, a component consisting of an outer joint member, an inner joint member, a ball and a cage from among a large number of outer joint members, inner joint members, balls and cages so that the PCD clearance and the like are within the specified value range. In consideration of these combinations, the outer joint member, the inner joint member, the ball and the cage are selected and combined (for example, see Patent Documents 1 and 2).
Japanese Patent Publication No. 1-55688 JP-A-63-34323
  By the way, the outer joint member and the inner joint member, which are the components of the conventional constant velocity universal joint described above, are manufactured by forging, turning, and heat treatment, and finally finishing the track groove such as grinding. Yes. In this way, when finishing the track groove after forging, turning and heat treatment, the cost of equipment, tools, etc. for finishing the track groove is increased, and the finishing process takes time, There was an inconvenience that the yield of the material was poor.
  Further, conventionally, when an internal part composed of an inner joint member, a ball and a cage is incorporated into the outer joint member, the PCD clearance, etc., has a specified value from a number of outer joint members, inner joint members, balls and cages. The components including the outer joint member, the inner joint member, the ball, and the cage are selected and combined so as to be within the range. This selective combination has a problem that it takes time to assemble each component and the workability is poor.
  By the way, a structure in which the shaft end of the shaft is press-fitted into the shaft hole inner diameter of the inner joint member is employed for the connection structure between the constant velocity universal joint and the shaft. A female spline is formed as irregularities along the axial direction on the inner diameter of the shaft hole of the inner joint member, and a male spline is also formed on the outer diameter of the shaft end of the shaft.
  The inner hole of the inner joint member in which the female spline is formed and the outer diameter of the shaft end of the shaft in which the male spline is formed are subjected to a hardening process by, for example, induction hardening or carburizing hardening to form a hardened layer. Yes. By forming this hardened layer, the strength of the inner diameter of the shaft hole of the inner joint member and the outer diameter of the shaft end of the shaft is ensured.
  The shaft is fitted to the inner joint member by press-fitting the shaft end outer diameter of the shaft into the shaft hole inner diameter of the inner joint member and meshing the male spline and the female spline. Torque can be transmitted between the shaft and the inner joint member by spline fitting. In such a fitting structure between the inner joint member of the constant velocity universal joint and the shaft, a hardened female spline is formed on the inner diameter of the shaft hole of the inner joint member, and the outer end diameter of the shaft is hardened. By forming the male spline, the shaft end outer diameter of the shaft is press-fitted into the shaft hole inner diameter of the inner joint member to be fitted with the spline.
  Further, in such a connection structure of the inner joint member and the shaft, the retaining ring having a round cross section attached to the shaft end portion of the shaft comes into contact with a locking surface provided on the inner joint member. There is something that was stopped.
  However, in such a fitting structure, since it is uneven fitting by the hardened female spline and the hardened male spline, there is a problem that play is likely to occur. It is difficult to reliably transmit the rotational torque, and when the torque is intermittently applied, the tooth surfaces of the spline are rubbed together, and the fatigue strength of the spline may be reduced. In addition, there is a possibility that abnormal noise may occur due to the play.
  In addition, if a retaining ring is provided in the connecting structure of the inner joint member and the shaft, a groove processing for fitting the retaining ring of the shaft and a locking surface processing of the inner joint member are required, which increases the number of steps and increases the stoppage. Since a ring is necessary, the number of parts is increased, leading to an increase in product cost.
Therefore, the present invention has been proposed in view of the above-mentioned problems, and the object is as follows.
Simplified manufacturing of the outer joint member or inner joint member to reduce the cost, and it is difficult to generate backlash at the shaft connection part, and an uneven fitting structure that can firmly connect the inner joint member and the shaft. It is in providing the constant velocity universal joint which has.
  A first constant velocity universal joint of the present invention includes an outer joint member, an inner joint member inserted into the outer joint member, and a torque transmission ball that is interposed between the outer joint member and the inner joint member to transmit torque. And a cage for holding a torque transmission ball, wherein at least one of the track groove of the outer joint member or the track groove of the inner joint member is formed by cold forging, and the outer joint Assemble the components consisting of the member, inner joint member, ball and cage by random matching, and connect the inner joint member and the shaft inserted into the shaft hole of the inner joint member via the concave-convex fitting structure, The entire fitting contact region between the convex portion of either the member or the shaft and the concave portion of the mating member fitted to the convex portion is in close contact.
  Each component is combined by random matching, and at least one of the track groove of the outer joint member or the track groove of the inner joint member is formed by cold forging finishing. As a result, only the cold forging finish is performed for the formation of the track grooves, and the conventional grinding and finishing after the heat treatment are unnecessary, so the cost of the constant velocity universal joint can be reduced. .
  Here, “random matching” refers to the outer joint member, the inner joint member, and the like so that the PCD clearance and the like are within a specified value range from among a large number of outer joint members, inner joint members, balls and cages. It means that the outer joint member and the inner joint member in which the track grooves are formed by cold forging finish are arbitrarily combined without selecting and combining the components including the ball and the cage.
  Since the entire fitting contact site between the convex portion and the concave portion of the mating member that fits into the convex portion is in close contact with each other, this fitting structure does not form a gap in which play occurs in the radial direction and the circumferential direction. For this reason, rattling can be suppressed to the minimum necessary by making the PCD clearance fall within the range of the specified value. If cold forging finish and random matching (no matching) are performed without tight fitting the inner joint member and the shaft, the total play is increased. For this reason, it is difficult to apply random matching when tight fitting is not employed.
  The second constant velocity universal joint of the present invention includes an outer joint member, an inner joint member inserted into the outer joint member, and a torque transmission ball that is interposed between the outer joint member and the inner joint member to transmit torque. And a constant velocity universal joint provided with a cage for holding a torque transmission ball, at least one of the track groove of the outer joint member or the track groove of the inner joint member is formed by cold forging, and a PCD clearance, etc. The shaft is inserted into the inner joint member and the shaft hole of the inner joint member while selecting and assembling the components including the outer joint member, the inner joint member, the ball, and the cage so that the value falls within the specified value range. Are connected via a concave-convex fitting structure, and the fitting contact portion between the convex portion of either the inner joint member or the shaft and the concave portion of the mating member fitted to the convex portion. In which whole is in close contact.
  That is, the inner joint member and the shaft are connected by fitting (tight fitting fitting) in which the entire contact area of the mating contact with the concave portion of the mating member fitted to the convex portion is tightly coupled, so that the radial direction and the circumference There is no gap in which play occurs in the direction. In this case, since each component is selected and assembled, the PCD clearance or the like can be easily kept within the specified value range, and the backlash between the components can be suppressed to the minimum necessary.
  As constant velocity universal joints, even fixed types such as Barfield type constant velocity universal joints (BJ) and undercut free type constant velocity universal joints (UJ), double offset type constant velocity universal joints (DOJ), etc. A sliding type may be used. In BJ, the entire area of each track groove is curved, and in UJ, one end of each track groove is in a straight shape parallel to the axis.
  In the concave / convex fitting structure between the inner diameter shaft hole of the inner joint member and the shaft, there is no gap formed in the radial direction and the circumferential direction, and the track groove of the outer joint member and the track of the inner joint member cooperating therewith are formed. It is desirable that the PCD clearance of the ball track formed by the groove be −0.02 to +0.3 mm. If it does in this way, it will become possible to suppress the backlash between each component which consists of an outer joint member, an inner joint member, a shaft, a ball | bowl, and a cage to required minimum. In particular, by setting the tight fit fitting and the PCD clearance in this way, the backlash can be suppressed to the minimum necessary. If the PCD clearance is smaller than -0.02 mm, it is difficult to ensure the operability of the constant velocity universal joint. Conversely, if it is larger than +0.3 mm, the clearance between the inner joint member and the shaft is difficult. Even if the backlash is eliminated, the total backlash of the constant velocity universal joint increases, and there are concerns about problems such as torque transmission loss and abnormal noise caused by the total backlash.
  The cross-sectional shapes of the track grooves of the outer joint member and the track grooves of the inner joint member are preferably Gothic arch shapes that are in angular contact with the ball. In this way, it is possible to stabilize the contact state of the ball with the track groove.
  A convex portion extending in the axial direction provided on one of the outer diameter surface of the shaft and the inner diameter surface of the shaft hole of the inner joint member is press-fitted into the other along the axial direction, and the convex portion is projected on the other. A recess is formed that fits closely to the part. In other words, the shape of the convex portion is transferred to the concave portion forming surface on the other side. At this time, the convex portion bites into the concave-part forming surface on the other side, so that the shaft hole is slightly expanded in diameter, allowing the convex portion to move in the axial direction and stopping the axial movement. In this case, the diameter of the shaft hole is reduced to return to the original diameter. Thereby, the whole fitting contact site | part with a convex part and the recessed part of the other party member fitted to the convex part closely_contact | adheres.
  The shaft is provided with a convex portion, and at least the hardness of the axial end portion of the convex portion is made higher than the inner diameter portion of the inner joint member so that the shaft extends into the axial hole of the inner joint member. By press-fitting from the part side, a concave part that closely fits to the convex part may be formed on the inner surface of the shaft hole of the inner joint member. Further, a convex portion is provided on the inner diameter surface of the shaft hole of the inner joint member, and at least the hardness of the end portion in the axial direction of the convex portion is made higher than the outer diameter portion of the shaft so that the convex portion on the inner joint member side is By press-fitting into the shaft from the axial end portion side, a concave portion that closely fits to the convex portion may be formed on the outer diameter surface of the shaft at the convex portion.
  It is preferable to provide a pocket portion for accommodating a protruding portion generated by forming the concave portion by the press-fitting. At this time, it is possible to provide the shaft with a pocket portion that accommodates the protruding portion that is generated by forming the concave portion by press fitting, or to provide the pocket portion on the inner diameter surface of the shaft hole of the inner joint member. Here, the protruding portion is a material portion of the capacity of the concave portion into which the fitting contact portion of the convex portion is fitted (fitted), and is extruded from the formed concave portion, or cut to form the concave portion. It is comprised from what was extruded, what was extruded, and what was cut.
  Further, a pocket portion for accommodating the protruding portion is provided on the press-fitting start end side of the convex portion of the shaft, and a collar portion for alignment with the shaft hole of the inner joint member is provided on the non-convex portion side of the pocket portion. Is preferred.
  Further, any portion in the protruding direction of the convex portion corresponds to the position of the concave portion forming surface before the concave portion is formed. At this time, the maximum diameter dimension of the arc connecting the vertices of the plurality of protrusions is made larger than the inner diameter dimension of the shaft hole of the inner joint member, and the maximum outer diameter dimension of the shaft outer diameter surface between the adjacent protrusions is set to the inner joint. Adjacent protrusions while making the inner diameter dimension of the shaft hole of the member smaller, or making the minimum diameter dimension of the arc connecting the apexes of the protrusions of the shaft hole smaller than the outer diameter dimension of the inner joint member fitting insertion part of the shaft In some cases, the minimum inner diameter of the inner surface of the shaft hole is made larger than the outer diameter of the inner joint member fitting insertion portion of the shaft.
  It is preferable that the circumferential thickness of the protruding portion intermediate portion of the convex portion is smaller than the circumferential dimension at a position corresponding to the intermediate portion between the convex portions adjacent in the circumferential direction. By setting in this way, the sum of the circumferential thicknesses of the projecting direction intermediate portions of the convex portions is the position corresponding to the intermediate portion in the mating convex portion that fits between the convex portions adjacent in the circumferential direction. Smaller than the sum of the circumferential thicknesses.
  It is also preferable to provide a concavo-convex portion along the axial direction in at least a part of the convex portion in the axial direction. Moreover, the uneven | corrugated | grooved part along the axial direction by the side of the said convex part may be formed in a sawtooth shape.
  In the present invention, a constant velocity universal joint in which components including an outer joint member, an inner joint member, a ball and a cage are assembled by random matching, and at least one of the track groove of the outer joint member or the track groove of the inner joint member is provided. Since it is formed by cold forging finishing, the track grooves of the outer joint member and inner joint member do not need to be turned or ground after heat treatment, so the equipment and tools required for the finishing process are not required. The processing time can be shortened, the outer joint member and the inner joint member can be efficiently manufactured, and the cost of the product can be reduced.
  In the concave / convex fitting structure between the inner diameter shaft hole of the inner joint member and the shaft, there is no gap between the radial direction and the circumferential direction, so that all of the fitting parts contribute to rotational torque transmission and stable rotational torque. Transmission is possible, and it is possible to avoid a decrease in the fatigue strength of the spline due to the friction of the spline tooth surfaces, resulting in excellent durability. Moreover, no abnormal noise is generated. Furthermore, since it is in close contact with each other in the radial direction and the circumferential direction, the strength of the torque transmitting portion is improved, and the constant velocity universal joint can be made lightweight and compact.
In the concave / convex fitting structure between the inner diameter shaft hole of the inner joint member and the shaft, there is no gap formed in the radial direction and the circumferential direction, and the track groove of the outer joint member and the track of the inner joint member cooperating therewith are formed. By reducing the PCD clearance of the ball track formed by the groove to -0.02 to +0.3 mm, the total play of the constant velocity universal joint can be reduced, thereby preventing torque transmission loss and abnormal noise from occurring. can do. The cross-sectional shape of the track groove is a Gothic arch shape, which stabilizes the contact state of the ball and enables smooth rotation transmission.
  A convex portion provided on either the outer diameter surface of the shaft or the inner diameter surface of the shaft hole of the inner joint member is press-fitted into the other along the axial direction, and the convex portion is closely fitted to the convex portion on the other side. A concave portion to be formed can be formed. For this reason, an uneven | corrugated fitting structure can be formed reliably. Moreover, it is not necessary to form a spline portion or the like on the member where the recess is formed, and it is excellent in productivity and does not require the phase alignment between the splines. Damage to the tooth surface can be avoided and a stable fitting state can be maintained.
  In addition, when the convex portion is provided on the shaft and the hardness on the convex portion side is made higher than the inner diameter portion of the shaft hole of the inner joint member, the concave portion is formed on the inner diameter surface of the inner joint member at the time of press-fitting. It becomes easy. Further, the shaft side hardness can be increased, and the torsional strength of the shaft can be improved. In addition, if a convex portion is provided on the inner diameter surface of the shaft hole of the inner joint member and the hardness of the axial end portion on the convex portion side is higher than the outer diameter portion of the shaft, It becomes easy to form a recess on the outer diameter surface. Since it is not necessary to perform hardness treatment (heat treatment) on the shaft side, the shaft productivity is excellent.
  By providing a pocket portion that accommodates the protruding portion generated by the depression formation by press-fitting, the protruding portion can be held (maintained) in this pocket, and the protruding portion is not mixed into the constant velocity universal joint. In other words, the protruding portion can be kept stored in the pocket portion, and it is not necessary to perform the removal processing of the protruding portion, the number of assembling work can be reduced, and the assembling workability can be improved and the cost can be reduced. Can be planned.
  In addition, by providing a collar for alignment on the axially anti-convex part side of the pocket part, the protruding part in the pocket part does not protrude to the collar part side, and the storage of the protruding part becomes more stable. . Moreover, since the collar portion is used for alignment, the shaft can be press-fitted into the inner joint member while preventing misalignment. For this reason, the inner joint member and the shaft can be connected with high accuracy, and stable torque transmission is possible.
  In addition, by arranging any part in the protruding direction of the convex part on the concave surface where the concave part is formed, the convex part bites into the concave part forming surface during press-fitting, and the concave part is reliably formed. can do.
  The convex part on the side where the concave part is formed by making the circumferential thickness of the intermediate part in the protruding direction of the convex part smaller than the dimension at the position corresponding to the intermediate part between the convex parts adjacent in the circumferential direction ( The thickness in the circumferential direction of the projecting intermediate portion of the convex portion between the concave portions formed can be increased. For this reason, the shear area of the convex part of the other party (the convex part having low hardness between the concave parts due to the formation of the concave parts) can be increased, and the torsional strength can be ensured. Moreover, since the tooth thickness of the convex portion on the higher hardness side is small, the press-fitting load can be reduced and the press-fitting property can be improved.
By providing a concavo-convex portion along the axial direction in at least a part of the axial direction on the convex side, the axial direction on the side having a small hardness (the side on which the concave portion to which the convex is fitted) is formed when press-fitted. The concavo-convex part along the line bites in along the axial direction. By this bite-in, it is possible to configure the shaft in the axial direction to prevent the inner joint member from coming off. Moreover, since the sawtooth bites into the side having a small hardness by making the uneven portion serrated, a stronger retaining mechanism is obtained. For this reason, the stable connection state can be maintained and the quality improvement of the constant velocity universal joint can be achieved. Moreover,
Since the stopper can be configured by the concave and convex portions along the axial direction, it is not necessary to provide a retaining ring fitting groove on the shaft and an inner joint member, thereby reducing the number of processing steps and the number of parts. Therefore, reduction in production cost and improvement in assembly workability can be achieved.
  Embodiments of the present invention are described in detail below. In addition, although the following embodiment illustrates the case where it applies to a fixed type (Barfield type) constant velocity universal joint (BJ), as mentioned later, other fixed type constant velocity universal joints, for example, an undercut free type The present invention can be applied to a constant velocity universal joint (UJ), and can also be applied to a double offset type constant velocity universal joint (DOJ) which is a sliding type constant velocity universal joint.
  1 and 3 illustrate the overall configuration of the bar field type constant velocity universal joint according to the first embodiment. The constant velocity universal joint includes an outer ring 1 as an outer joint member, an inner ring 2 as an inner joint member into which the outer ring 1 is inserted, and a torque transmission member that is interposed between the outer ring 1 and the inner ring 2 to transmit torque. And a cage 4 that is interposed between the outer ring 1 and the inner ring 2 and holds the ball 3 as main members. When this fixed type constant velocity universal joint is applied to a drive shaft, the outer ring 1 is connected to a wheel bearing device (not shown) and the shaft 5 is connected to the inner ring 2 with the concave-convex fitting structure M. Torque is transmitted at a constant speed even when the rotation axis of the inner ring 2 is angled.
  The outer ring 1 includes a mouse portion 6 and a stem portion 7. The stem portion 7 is coupled to the wheel bearing device so as to be able to transmit torque. The mouse portion 6 has a bowl shape opened at one end, and a plurality of track grooves 9 extending in the axial direction are formed on the inner spherical surface (inner circumferential surface) 8 at equal intervals in the circumferential direction. The track groove 9 extends to the open end of the mouse portion 6. In the inner ring 2, a plurality of track grooves 11 extending in the axial direction are formed on the outer spherical surface (outer circumferential surface) 10 at equal intervals in the circumferential direction. The track groove 11 is cut in the axial direction of the inner ring 2.
  The track groove 9 of the outer ring 1 and the track groove 11 of the inner ring 2 form a pair so that the ball 3 as a torque transmitting element can roll on the ball track constituted by each pair of track grooves 9 and 11. It is incorporated. The ball 3 is interposed between the track groove 9 of the outer ring 1 and the track groove 11 of the inner ring 2 and transmits torque. The cage 4 is slidably interposed between the outer ring 1 and the inner ring 2, is in contact with the inner spherical surface 8 of the outer ring 1 at the outer spherical surface 4a, and is in contact with the outer spherical surface 10 of the inner ring 2 at the inner spherical surface 4b.
In the constant velocity universal joint, components including the outer ring 1, the inner ring 2, the ball 3 and the cage 4 are assembled by random matching, and the track groove 9 of the outer ring 1 and the track groove 11 of the inner ring 2 are formed by cold forging.
  That is, the constituent elements including the outer ring 1, the inner ring 2, the ball 3, and the cage 4 so that the PCD clearance and the like are within the specified value range from among the plurality of outer rings 1, inner rings 2, balls 3, and cages 4. The selected combination is not performed and the combination is made by random matching that arbitrarily combines the outer ring 1 and the inner ring 2 in which the track grooves 9 and 11 are formed by cold forging.
  Thus, each component is combined by random matching, and at least one of the track groove 9 of the outer ring 1 or the track groove 11 of the inner ring 2 is formed by cold forging, and only cold forging finish is performed, Since no grinding or finishing after heat treatment is required, the cost of the constant velocity universal joint can be reduced.
  It is also possible to select and assemble the components consisting of the outer ring 1, the inner ring 2, the ball 3 and the cage 4 so that the PCD clearance is within the specified value range. In this case, the PCD clearance can be easily set. It can be within the range of the specified value, and the backlash between each component can be suppressed to the minimum necessary.
  As described above, the inner ring 2 is coupled to the shaft 5 so that torque can be transmitted by press-fitting the end portion 5a of the shaft 5 into the shaft hole 22 thereof. That is, the shaft 5 and the inner ring 2 are connected via the concave-convex fitting structure M according to the first embodiment of the present invention. The inner diameter surface 37 (see FIG. 2) of the shaft hole 22 of the inner ring 2 is formed by cold forging finishing, but may be formed by turning or polishing finishing.
  As shown in FIG. 4, the concave-convex fitting structure M includes, for example, a convex portion 35 provided on the shaft 5 side and extending in the axial direction, and a concave portion 36 formed in the inner diameter surface 37 of the shaft hole 22 of the inner ring 2. Thus, the entire fitting contact portion 38 between the convex portion 35 and the concave portion 36 of the inner ring 2 fitted to the convex portion 35 is in close contact. A plurality of convex portions 35 are arranged at a predetermined pitch along the circumferential direction, and a plurality of concave portions 36 into which the convex portions 35 are fitted to the inner diameter surface 37 of the inner ring 2 are formed along the circumferential direction. That is, the convex part 35 and the concave part 36 fitted to this are tight-fitted over the entire circumference in the circumferential direction.
In this case, any part in the protruding direction of the convex portion (in the drawing, the intermediate portion in the protruding direction) corresponds to the position of the concave portion forming surface before the concave portion is formed. That is, each convex portion 35 has a triangular shape (mountain shape) having a convex round-shaped cross section, and the fitting contact portion 38 between each convex portion 35 and the concave portion 36 of the inner ring 2 is shown in FIG. It is the range A shown in b), and is the range from the mid-section of the mountain in the cross section to the summit. Further, a gap 40 is formed on the inner diameter side with respect to the inner diameter surface 37 of the inner ring 2 between the adjacent convex portions 35 in the circumferential direction. In addition, a part (for example, front-end | tip part) may respond | correspond, without the protrusion direction intermediate part of the convex part 35 corresponding to the position of the recessed part formation surface before recessed part formation.
  Here, in the concave / convex fitting structure M between the inner diameter shaft hole 22 of the inner ring 2 and the shaft 5, no gap is formed in which the play occurs in the radial direction and the circumferential direction, and at least one of the tracks described above is cold forged. In the constant velocity universal joint having the finished outer ring 1 and inner ring 2, the PCD clearance of the ball track formed by the track groove 9 of the outer ring 1 and the track groove 11 of the inner ring 2 cooperating therewith is -0.02. It is defined as +0.3 mm. In this way, it is possible to suppress the backlash between the constituent elements including the outer ring 1, the inner ring 2, the shaft 5, the ball 3, and the cage 4 to the minimum necessary.
  By the way, as shown in FIG. 5 and FIG. 6, the outer diameter portion of the end portion 5a of the shaft 5 is subjected to a thermosetting treatment, and the spline comprising the convex portions 41a and the concave portions 41b along the axial direction on the hardened layer S. 41 is formed. For this reason, the convex part 41a of the spline 41 is cured, and the convex part 41a becomes the convex part 35 of the concave-convex fitting structure M. As this thermosetting treatment, various heat treatments such as induction hardening and carburizing and quenching can be employed. Here, induction hardening is a hardening method that applies the principle that superheats a conductive object by placing a part necessary for hardening in a coil through which high-frequency current flows and generating Joule heat by electromagnetic induction. is there. The carburizing and quenching is a method in which carbon is infiltrated / diffused from the surface of the low carbon material and then quenched. In FIGS. 5 and 6, the hatched portion indicated by a broken line indicates the hardened layer S.
  Further, as shown in FIGS. 2 and 4, the inner ring 2 has a hardened layer S1 (cross-hatched portion) formed by induction hardening on the outer spherical surface between the track grooves and the track grooves, and the inner diameter surface 37 of the shaft hole 22 is not formed. It is supposed to be cured. If induction hardening is performed, the surface is hard and the inside can be kept with the hardness of the material, and the inner diameter side of the inner ring 2 can be maintained in an unhardened state. The hardness difference between the hardened layer S of the shaft 5 and the uncured portion of the inner diameter surface 37 of the shaft hole 22 of the inner ring 2 is 30 points or more in HRC. The module of the spline 41 of the shaft 5 is a small tooth of 0.5 or less. Here, the module is a pitch circle diameter divided by the number of teeth.
  Any part of the projecting direction of the convex portion 35 corresponds to the position of the concave portion forming surface (in this case, the inner diameter surface 37 of the shaft hole 22 of the inner ring 2) before the concave portion is formed. That is, as shown in FIG. 2, the inner diameter dimension D of the inner diameter surface 37 of the shaft hole 22 is the maximum outer diameter dimension of the convex section 35, that is, the circle connecting the vertices of the convex section 35 which is the convex section 41a of the spline 41. It is smaller than the maximum diameter dimension (circumscribed circle diameter) D1, and is set larger than the maximum outer diameter dimension of the shaft outer diameter surface between adjacent convex portions, that is, the maximum diameter dimension D2 of the circle connecting the bottoms of the concave portions 41b of the spline 41. The That is, D2 <D <D1. The spline 41 can be formed by various processing methods such as rolling processing, cutting processing, press processing, and drawing processing, which are known publicly known means.
  Next, a fitting method of the uneven fitting structure M will be described. First, as shown in FIG. 2, the shaft 5 is inserted (press-fitted) into the inner ring 2 in a state where the axis of the inner ring 2 and the axis of the shaft 5 are aligned. At this time, the inner diameter dimension D of the inner diameter surface 37 of the shaft hole 22, the maximum outer diameter dimension D1 of the projection 35, and the maximum diameter dimension (maximum outer diameter dimension) D2 of the recess of the spline 41 are as described above. Moreover, since the hardness of the convex portion 35 is 30 points or more larger than the hardness of the inner diameter surface 37 of the shaft hole 22, if the shaft 5 is press-fitted into the shaft hole 22 of the inner ring 2, the convex portion 35 becomes the inner diameter surface. 37, the convex portion 35 forms a concave portion 36 into which the convex portion 35 is fitted along the axial direction.
  As a result, as shown in FIGS. 4A and 4B, a fitting state in which the entire fitting contact portion 38 between the convex portion 35 of the end portion 5a of the shaft 5 and the concave portion 36 of the inner ring 2 is in close contact is configured. can do. That is, the concave-convex fitting structure M can be formed by transferring the shape of the convex portion 35 to the counterpart concave-portion forming surface (in this case, the inner diameter surface 37 of the shaft hole 22).
  In the present invention, each component is combined by random matching, and the track groove 9 of the outer ring 1 or the track groove 11 of the inner ring 2 is formed by cold forging, so that only cold forging finish is performed, and after turning or heat treatment No grinding finish is required. This eliminates the need for equipment and tools required for the finishing process, shortens the machining time, allows the outer ring and inner ring to be efficiently manufactured, and reduces the cost of the product. .
  In the concave / convex fitting structure M, since the entire fitting contact portion 38 of the convex portion 35 and the concave portion 36 of the inner ring 2 is in close contact with each other, in the concave / convex fitting structure M, a gap in which play occurs in the radial direction and the circumferential direction. Is not formed. For this reason, all of the fitting parts contribute to rotational torque transmission, and stable rotational torque transmission is possible. A decrease in the fatigue strength of the spline due to friction of the tooth surfaces of the spline can be avoided, and the durability is excellent. Moreover, no abnormal noise is generated. Furthermore, since it is in close contact with each other in the radial direction and the circumferential direction, the strength of the torque transmitting portion is improved, and the constant velocity universal joint can be made lightweight and compact.
  Further, in the concave / convex fitting structure M between the inner diameter shaft hole 22 of the inner ring 2 and the shaft 5, there is no gap between which the play occurs in the radial direction and the circumferential direction, and the track groove 9 of the outer ring 1 and the inner ring that cooperates therewith. Since the PCD clearance of the ball track formed by the two track grooves 11 is defined as -0.02 to +0.3 mm, each component including the outer ring 1, the inner ring 2, the shaft 5, the ball 3, and the cage 4 As a result, it is possible to reduce the backlash between the constant velocity universal joints, thereby reducing the total backlash of the constant velocity universal joint and preventing the occurrence of torque transmission loss and abnormal noise. In this case, if the PCD clearance is smaller than −0.02 mm, it is difficult to ensure the operability of the constant velocity universal joint. Conversely, if the PCD clearance is larger than +0.3 mm, there is a backlash between the components. growing. If cold forging finish and random matching (no matching) are performed without tight fitting the inner joint member and the shaft, the total play is increased. For this reason, it is difficult to apply random matching when tight fitting is not employed.
  At least one of the track groove 9 of the outer ring 1 or the track groove 11 of the inner ring 2 is formed by cold forging, and the components including the outer ring 1, the inner ring 2, the shaft 5, the ball 3 and the cage 4 are selected and assembled. If this is the case, the PCD clearance can easily be within the range of the specified value. It is also possible to make the PCD clearance smaller than the upper limit of +0.3 mm, which is connected to the inner ring 2 through the concave / convex fitting structure M between the inner diameter shaft hole 22 and the shaft 5, and the convex portion 35. If the entire contact area of the mating contact with the concave portion 36 of the mating member fitted to the convex portion 35 is brought into close contact, the total play can be further reduced.
  As in the above-described embodiment, the spline 41 formed on the shaft 5 uses small teeth with a module of 0.5 or less, so that the moldability of the spline 41 can be improved and the press-fit load can be reduced. Can be planned. In addition, since the convex part 35 can be comprised with the spline normally formed in this kind of shaft, this convex part 35 can be easily formed at low cost.
  Further, when the concave portion 36 is formed by press-fitting the shaft 5 into the inner ring 2, work hardening occurs on the concave portion 36 side. Here, work hardening means that when plastic deformation (plastic processing) is applied to an object, the resistance to deformation increases as the degree of deformation increases, and it becomes harder than a material that has not undergone deformation. For this reason, the inner diameter surface 37 of the inner ring 2 on the concave portion 36 side is hardened by the plastic deformation that occurs during the press-fitting, and the rotational torque transmission performance can be improved.
  By the way, in the spline 41 shown in FIG. 4, the pitch of the convex portions 41a and the pitch of the concave portions 41b are set to be the same. For this reason, in the said embodiment, as shown in FIG.4 (b), it corresponds to the said intermediate part between the circumferential direction thickness L of the protrusion direction intermediate part of the convex part 35, and the convex part 35 adjacent to the circumferential direction. The circumferential dimension L0 at the position is substantially the same.
  On the other hand, as shown in FIG. 7, the circumferential thickness L2 of the projecting direction intermediate portion of the convex portion 35 is set to the circumferential dimension at a position corresponding to the intermediate portion between the convex portions 35 adjacent in the circumferential direction. It may be smaller than L1. That is, in the spline 41 formed on the shaft 5, the circumferential thickness (tooth thickness) L <b> 2 of the intermediate portion in the protruding direction of the convex portion 35 is set to the convex portion 43 on the opposite side, that is, the inner ring 2 side. This is smaller than the circumferential thickness (tooth thickness) L1 of the intermediate portion in the protruding direction.
  Therefore, the total tooth thickness (ΣB1 + B2 + B3 +...) Of the convex portions (convex teeth) 35 on the shaft 5 side is smaller than the total tooth thickness (ΣA1 + A2 + A3 +...) Of the convex portions 43 on the entire circumference on the inner ring 2 side. It is set. As a result, the shear area of the convex portion 43 on the inner ring 2 side can be increased, and the torsional strength can be ensured. And since the tooth thickness of the convex part 35 is small, a press-fit load can be made small and a press-fit property can be aimed at. When making the sum total of the circumferential thickness of the convex part 35 smaller than the sum total of the circumferential direction thickness in the other convex part 43, the circumferential direction thickness L2 of all the convex parts 35 is the convex part adjacent to the circumferential direction. It is not necessary to make it smaller than the circumferential dimension L1 between 35. That is, among the plurality of convex portions 35, even if the circumferential thickness of the arbitrary convex portion 35 is the same as the circumferential dimension between the convex portions adjacent in the circumferential direction, it is larger than the circumferential dimension. However, it is sufficient if the sum is small. 7 has a trapezoidal cross section (Mt. Fuji shape).
  Next, FIG. 8 shows a second embodiment, and this concave-convex fitting structure M has a convex portion 35 of the shaft 5, that is, a convex portion 41 a of the spline 41, and a concave-convex portion 55 extending in the axial direction partially in the axial direction. Is formed. In this case, the uneven portion 55 is formed in a sawtooth shape along the axial direction. In this case, the convex portion (convex tooth) 55a has a cross-sectional shape of a right triangle having the pocket side as an inclined surface.
  As shown in FIG. 10, if the shaft 5 having the concave and convex portion 55 is press-fitted into the shaft hole 22 of the inner ring 2 by aligning the axial center of the inner ring 2 and the shaft 5, the convex portion on the shaft 5 side. In this case, the concave / convex portion 55 bites into the bottom of the concave portion 36 formed on the inner ring 2 side. That is, the diameter of the shaft hole 22 of the inner ring 2 that has been expanded at the time of press-fitting is increased, but when the press-fitting is completed, the diameter is reduced to return to the original state. For this reason, a pressing force (diameter reducing force) acts on the concave and convex portion 55 from the inner diameter side of the shaft hole 22 of the inner ring 2 as shown by the arrows in FIG. The convex part 55a of the part 55 bites in.
  By providing the projections and depressions 55 along the axial direction in at least a part of the projections 35 in the axial direction, the side having a small hardness when pressed-in (the depressions 36 into which the projections 35 are fitted is formed. The concavo-convex portion 55 along the axial direction bites in the axial direction. By this bite-in, it is possible to constitute an axial stopper of the shaft 5 with respect to the inner joint member. Further, by making the concave and convex portion 55 serrated, the sawtooth bites more into the side having a low hardness, so that a stronger retaining mechanism is obtained. For this reason, the stable connection state can be maintained and the quality improvement of the constant velocity universal joint can be achieved. Moreover, since the concave and convex portions 55 along the axial direction can be configured to prevent slipping, it is not necessary to provide a retaining surface for the retaining ring fitting groove and the inner joint member on the shaft 5, and the number of processing steps and the number of parts can be reduced. Can be reduced, and production costs can be reduced and assembly workability can be improved.
  By the way, if the shaft 5 is press-fitted into the inner ring 2, the material protrudes from the concave portion 36 formed by the convex portion 35, and the protruding portion 45 as shown in FIG. 11 is formed. The protruding portion 45 is a material component of the capacity of the concave portion 36 into which the fitting contact portion 38 of the convex portion 35 is fitted (fitted), and is pushed out from the formed concave portion 36 to form the concave portion 36. It is composed of what has been cut or both extruded and cut.
  For this reason, in the constant velocity universal joint shown in FIG. 1, after the shaft 5 is assembled to the inner ring 2, it is necessary to remove the protruding portion 45. Therefore, in another embodiment shown in FIG. 11, a pocket portion 50 that accommodates the protruding portion 45 is provided in the shaft 5.
  That is, the pocket portion 50 is formed by providing the circumferential groove 51 at the axial end edge of the spline 41 of the shaft 5. As shown in FIG. 12, in the circumferential groove 51, the side wall 51a on the spline 41 side is a plane orthogonal to the axial direction, and the side surface 51b on the anti-spline side faces from the groove bottom 51c to the anti-spline side. This is a tapered surface that expands in diameter.
  Further, a disc-shaped flange 52 for alignment is provided on the side opposite to the spline from the side surface 51b. The outer diameter dimension of the flange 52 is set to be the same as the hole diameter of the shaft hole 22 or slightly smaller than the hole diameter (inner diameter dimension) D of the shaft hole 22. In this case, a minute gap t is provided between the outer diameter surface 52 a of the flange 52 and the inner diameter surface 37 of the shaft hole 22.
  Even in the case of the inner ring 2 shown in FIG. 11, as shown in FIG. 13, if the shaft center of the inner ring 2 and the shaft center of the shaft 5 are aligned and the shaft 5 is press-fitted into the shaft hole 22 of the inner ring 2. The concave portion 36 is formed on the inner ring 2 side by the convex portion 35 on the shaft 5 side. At this time, the protruding portion 45 produced is housed in the pocket portion 50 while curling as shown in FIG.
In this way, by providing the pocket portion 50 for storing the protruding portion 45 generated by forming the concave portion by the press-fitting, the protruding portion 45 can be held (maintained) in the pocket portion 50, and the constant velocity universal joint is provided. There is no misunderstanding. That is, the protruding portion 45 can be kept stored in the pocket portion 50, and it is not necessary to perform the removal process of the protruding portion 45, the number of assembling operations can be reduced, and the assembling workability can be improved. Cost reduction can be achieved.
  Further, by providing a collar portion 52 for alignment with the shaft hole 22 of the inner ring 2 on the side opposite to the convex portion of the pocket portion 50, the protruding portion 45 in the pocket portion 50 does not protrude to the collar portion 52 side. , The storage of the protruding portion 45 becomes more stable. Moreover, since the flange portion 52 is used for alignment, the shaft portion can be press-fitted into the shaft hole 22 of the inner ring 2 while preventing misalignment. For this reason, the inner ring 2 and the shaft 5 can be connected with high accuracy, and stable torque transmission is possible.
  Since the flange 52 is used for aligning during press-fitting, the outer diameter is preferably set to be slightly smaller than the hole diameter of the inner ring 2. That is, if the outer diameter dimension of the flange 52 is the same as the hole diameter of the inner ring 2 or larger than the hole diameter of the inner ring 2, the flange 52 itself is press-fitted into the shaft hole of the inner ring 2. At this time, if the center is misaligned, the convex portion 35 of the concave-convex fitting structure M is press-fit as it is, and the shaft 5 and the inner ring 2 are connected in a state where the axis of the shaft 5 and the axis of the inner ring 2 do not match. Will be. Moreover, if the outer diameter dimension of the collar part 52 is too smaller than the hole diameter of a shaft hole, it will not function for centering. For this reason, it is preferable that the minute gap t between the outer diameter surface 52a of the flange portion 52 and the inner diameter surface of the shaft hole is set to about 0.01 mm to 0.2 mm.
  Since the other structure of the constant velocity universal joint shown in FIG. 11 is the same as that of the constant velocity universal joint shown in FIG. 1, the same members as those in FIG. For this reason, the constant velocity universal joint shown in FIG. 11 has the same effect as the constant velocity universal joint shown in FIG.
  Incidentally, as shown in FIGS. 14 and 15, small concave portions 60 arranged at a predetermined pitch along the circumferential direction may be provided on the inner diameter surface of the shaft hole 22 of the inner ring 2. The small recess 60 needs to be smaller than the volume of the recess 36. Thus, by providing the small recessed part 60, the press fit property of the convex part 35 can be improved. That is, by providing the small concave portion 60, the capacity of the protruding portion 45 formed when the convex portion 35 is press-fitted can be reduced, and the press-fit resistance can be reduced. Moreover, since the protrusion part 45 can be decreased, the volume of the pocket part 50 can be made small and the workability of the pocket part 50 and the improvement of the intensity | strength of the shaft 5 can be aimed at. In addition, although the shape of the small recessed part 60 is a semi-elliptical shape in the example of a figure, other various things, such as a rectangle, can be employ | adopted and a number can also be set arbitrarily.
  As shown in FIG. 16, the cross-sectional shape of the track groove 9 of the outer ring 1 and the track groove 11 of the inner ring 2 may be a Gothic arch shape that makes angular contact with the ball 3. The track grooves 9 and 11 having the Gothic arch shape have two ball contact points P and Q (ball contact angle α) that make angular contact with the ball 3. Such angular contact is suitable in that the contact state of the ball 3 with the track grooves 9 and 12 is stabilized. That is, the cross-sectional shape of the track grooves 9 and 12 is a Gothic arch shape to stabilize the contact state of the ball and enable smooth rotation transmission.
  FIG. 17 shows a second embodiment. This constant velocity universal joint is an undercut free type constant velocity universal joint (UJ), and a plurality of track grooves 72 are provided in the circumferential direction or the like on an inner spherical surface (inner circumferential surface) 71. An outer ring 73 as an outer joint member formed along the axial direction at intervals, and a plurality of track grooves 75 paired with the track grooves 72 of the outer ring 73 on the outer spherical surface (outer peripheral surface) 74 are arranged at equal intervals in the circumferential direction. An inner ring 76 as an outer joint member formed along the direction, a plurality of balls 77 that transmit torque between the track groove 72 of the outer ring 73 and the track groove 75 of the inner ring 76, and the inner ring 73 A cage 78 is provided between the spherical surface 71 and the outer spherical surface 74 of the inner ring 76 to hold a ball 77 as a torque transmission member.
  The track groove 72 of the outer ring 73 includes a back side track groove 72a in which the track groove bottom is an arc portion and an opening side track groove (straight groove) 72b in which the track groove bottom is a straight portion parallel to the outer ring axis. The track groove 75 of the inner ring 76 includes a back side track groove 75a in which the track groove bottom is a straight portion parallel to the outer ring axis and an opening side track groove 75b in which the track groove bottom is an arc portion.
  FIG. 18 shows a third embodiment. This constant velocity universal joint is a DOJ type constant velocity universal joint, and a plurality of linear track grooves 82 extending in the axial direction are provided on the cylindrical inner peripheral surface 84 in the circumferential direction. An outer ring 80 as an outer joint member formed at equal intervals and a plurality of linear track grooves 92 extending in the axial direction in pairs with the track grooves 82 of the outer ring 80 are formed on the spherical outer peripheral surface 94 at equal intervals in the circumferential direction. The formed inner ring 90 as an inner joint member, a plurality of balls 100 interposed between the track groove 82 of the outer ring 80 and the track groove 92 of the inner ring 90 and transmitting torque, and the cylindrical inner peripheral surface of the outer ring 80 84 and a cage 101 that holds the ball 100 interposed between the spherical outer peripheral surface 94 of the inner ring 90.
  As in the embodiment shown in FIG. 1, the outer rings 73 and 80 are the undercut-free type constant velocity universal joint (UJ) shown in FIG. 17 and the DOJ type constant velocity universal joint shown in FIG. The inner ring 76, 90, the balls 77, 100 and the cage 78, 101 are assembled by random matching, and the outer ring 73, 80 track grooves 72, 82 and the inner ring 76, 90 track grooves 75, 92 are cold forged. It is formed by finishing. Further, the PCD clearance of the ball track formed by the track grooves 72 and 82 of the outer rings 73 and 80 and the track grooves 75 and 92 of the inner rings 76 and 90 cooperating with the outer rings 73 and 80 is defined as -0.02 to +0.3 mm. ing. Furthermore, the cross-sectional shapes of the track grooves 72 and 82 of the outer rings 63 and 80 and the track grooves 75 and 92 of the inner rings 76 and 90 may be Gothic arch shapes that make angular contact with the ball 100.
  Further, the undercut-free constant velocity universal joint (UJ) shown in FIG. 17 or the DOJ type constant velocity universal joint shown in FIG. The shaft 5 is coupled by the uneven fitting structure M. As this uneven | corrugated fitting structure M, various structures, such as the said FIG.2 and FIG.4, FIG.7, FIG.8, FIG.14, are employable. Further, as shown in FIG. 11 to FIG. 13, a pocket portion for accommodating the protruding portion generated by forming the concave portion by press-fitting is provided, and further, an adjustment with the shaft hole of the inner joint member is provided on the side opposite to the convex portion of the pocket portion. A core collar can be provided.
  For this reason, even if it is an undercut-free type constant velocity universal joint (UJ) shown in FIG. 17 or the DOJ type constant velocity universal joint shown in FIG. Can do.
By the way, in each said embodiment, while forming the spline 41 which comprises the convex part 35 in the shaft 5 side, it hardens | cures with respect to the spline 41 of this shaft 5, and the internal diameter surface of the inner ring | wheel 2 is unhardened (raw material) ). On the other hand, as shown in FIGS. 19 and 20, while forming a spline 61 (consisting of ridges 61a and ridges 61b) subjected to hardening treatment on the inner diameter surface of the shaft hole 22 of the inner ring 2, The shaft 5 may not be subjected to a curing process. The spline 61 can also be formed by various processing methods such as broaching, cutting, pressing, and drawing, which are publicly known means. Further, various heat treatments such as induction hardening and carburizing and quenching can be employed as the thermosetting treatment.
  In this case, the intermediate portion in the protruding direction of the convex portion 35 corresponds to the position of the concave portion forming surface (the outer diameter surface of the shaft 5) before the concave portion is formed. That is, the minimum diameter (minimum inner diameter dimension of the convex portion 35) D4 of the circle connecting the apexes of the convex portions 35 that are the convex stripes 61a of the spline 61 is smaller than the outer diameter D3 of the shaft 5, and The minimum outer diameter dimension of the circle connecting the bottoms (the inner diameter dimension of the inner diameter surface of the shaft hole between the protrusions) D5 is set larger than the outer diameter dimension D3 of the shaft 5. That is, D4 <D3 <D5.
  In this case, if the shaft 5 is press-fitted into the shaft hole 22 of the inner ring 2, the concave portion 36 in which the convex portion 35 is fitted to the outer diameter surface 66 of the shaft 5 can be formed by the convex portion 35 on the inner ring 2 side. Accordingly, it is possible to configure a fitting state in which the entire fitting contact portion 38 between the convex portion 35 on the inner ring 2 side and the concave portion 36 of the shaft 5 is in close contact.
  Here, the fitting contact portion 38 between the convex portion 35 and the concave portion 36 of the shaft 5 is a range B shown in FIG. 20B, and is a range from the middle of the mountain shape to the top of the mountain in the cross section. Further, a gap 62 is formed on the outer diameter side of the outer peripheral surface of the shaft 5 between the adjacent convex portions 35 in the circumferential direction.
  Even in this case, since the protruding portion is formed by press-fitting, it is preferable to provide a pocket portion for storing the protruding portion. Unlike the one shown in FIG. 11, the protruding portion is formed on the shaft side, so that the pocket portion is provided on the inner ring 2 side.
  Thus, even if the convex portion 35 of the concave-convex fitting structure M is formed on the inner ring 2 side, the flange portion that serves as an alignment when the outer diameter dimension is press-fitted into the inner ring 2 at the end portion of the shaft 5 May be provided. Thereby, press-fitting with high accuracy becomes possible. In addition, you may provide uneven | corrugated | grooved parts, such as a sawtooth shape which exhibits a retaining function in the inner ring | wheel 2 side.
  Of course, the undercut-free type constant velocity universal joint (UJ) shown in FIG. 17 or the DOJ type constant velocity universal joint shown in FIG. The structure of forming may be sufficient.
  As described above, the embodiment of the present invention has been described. However, the present invention is not limited to the embodiment, and various modifications are possible. For example, as the shape of the convex portion 35 of the concave-convex fitting structure, FIG. In the embodiment shown in FIG. 7, the cross section is triangular, and in the embodiment shown in FIG. 7, the cross section is trapezoidal (mountain shape), but other shapes such as a semicircular shape, a semi-elliptical shape, and a rectangular shape are adopted. Further, the area and number of the convex portions 35, the circumferential arrangement pitch, and the like can be arbitrarily changed. That is, the splines 41 and 61 are formed, and the convex portions (convex teeth) 41a and 61a of the splines 41 and 61 do not need to be the convex portions 35 of the concave-convex fitting structure M. Alternatively, a curved corrugated mating surface may be formed. In short, the convex portion 35 disposed along the axial direction can be press-fitted into the mating side, and the concave portion 36 can be formed on the mating side with the convex portion 35 so as to closely fit the convex portion 35. It is only necessary that the entire fitting contact portion 38 between the portion 35 and the corresponding recess 36 is in close contact, and that rotational torque can be transmitted between the inner rings 2, 76, 90 and the shaft 5.
  Further, the shaft holes 22, 79, 93 of the inner rings 2, 76, 90 may be deformed holes such as polygonal holes other than circular holes, and the ends of the shaft 5 to be inserted into the shaft holes 22, 79, 93. The cross-sectional shape of the part 5a may also be an irregular cross section such as a polygon other than a circular cross section. Therefore, for example, the shaft holes 22, 79, 93 of the inner rings 2, 76, 90 are circular holes, the cross-sectional shape of the end portion 5a of the shaft 5 is a polygon other than a circle, and this edge portion is referred to as the convex portion 35. can do.
  As the shape of the pocket portion 50, in the above-described embodiment, the circumferential groove 51 has a side surface 51b on the side opposite to the spline that is a tapered surface that expands from the groove bottom 51c toward the side opposite to the spline. It is sufficient that the protruding portion 45 to be generated can be accommodated (accommodated), and as long as the capacity of the pocket portion 50 can be accommodated to the protruding portion 45 that is generated. .
  In the case where the concavo-convex portion 55 is provided, in FIG. 8, it is provided in the middle portion of the spline 41 in the axial direction. The spline 41 may be provided along the entire length in the axial direction. Moreover, the number and shape of the convex part (convex tooth) 55a of each uneven part 55 are also arbitrary. That is, as the concavo-convex portion 55, the concavo-convex portion 55 may be provided on the entire convex portion 35, or may be provided on an arbitrary convex portion 35 among the total convex portions 35. As shown in FIG. 11 etc., the uneven | corrugated | grooved part 55 may be provided in the shaft 5 which has the pocket part 50. As shown in FIG. In the embodiment, the concave and convex portion 55 is provided in the convex portion 41 a of the spline 41 constituting the convex portion 35, but the concave and convex portion 55 may be provided in the concave portion 41 b of the spline 41.
  Moreover, in the said embodiment, although the thermosetting process was performed with respect to the convex part 35 and the convex corresponding | compatible part side was made into the non-hardened part, the hardness of the convex part 35 was made higher than the site | part in which a recessed part is formed, hardness difference is made. If it can be applied, both of them may be heat treated or both may not be heat treated. Furthermore, since only the press-fitting start end portion of the convex portion 35 needs to be harder than the portion where the concave portion 36 is formed during press-fitting, it is not necessary to increase the overall hardness of the convex portion 35. Further, although the gap 40 is formed in FIG. 3 and the like, the gap 40 between the convex portions 35 may bite into the inner diameter surface 37 of the inner ring 2. As described above, the hardness difference between the convex portion 35 side and the concave portion forming surface formed by the convex portion 35 is preferably 30 points or more by HRC, but the convex portion 35 can be press-fitted. If there is, it may be less than 30 points. Examples of the heat treatment method include induction hardening, carburizing and quenching, tempering, and normalizing. In the case where the concave portion 36 is formed on the inner diameter surface of the inner ring 2 by the convex portion 35 of the shaft 5 at the time of press-fitting, when the inner ring 2 is carburized and quenched, the inner surface is subjected to a carbon-proof treatment so It becomes easy to form a low layer on the inner diameter surface of the inner ring 2. Further, when the concave portion 36 is formed on the shaft 5 by the convex portion 35 of the inner diameter of the inner ring 2 at the time of press-fitting, the shaft 5 is subjected to normalization treatment or tempering treatment, thereby ensuring the torsional strength of the shaft 5. The hardness of the outer diameter surface can be made lower than the convex portion 35 of the inner diameter of the inner ring 2.
  Although the end surface (press-fit start end) of the convex portion 35 is a surface orthogonal to the axial direction in the embodiment, it may be inclined at a predetermined angle with respect to the axial direction. In this case, it may be inclined from the inner diameter side toward the outer diameter side toward the anti-convex portion side or inclined toward the convex portion side. In addition, when press-fitting the convex portion 35, even if the side where the concave portion 36 is formed is fixed and the side where the convex portion 35 is formed is moved, the side where the convex portion 35 is formed is reversed. It may be fixed and the side where the recess 36 is formed may be moved or both may be moved.
It is a longitudinal cross-sectional view of the BJ type constant velocity universal joint which shows 1st Embodiment of this invention. It is sectional drawing of the decomposition | disassembly state of the said uneven | corrugated fitting structure. It is a cross-sectional view of the constant velocity universal joint. The uneven | corrugated fitting structure of the said constant velocity universal joint is shown, (a) is an expanded sectional view, (b) It is the X section enlarged view of (a). It is a principal part side view of the shaft connected with the said constant velocity universal joint. It is a front view of the shaft. It is a principal part expanded sectional view which shows the 1st modification of an uneven | corrugated fitting structure. It is sectional drawing which shows the 2nd modification of an uneven | corrugated fitting structure. It is a principal part expanded sectional view of the uneven | corrugated fitting structure of the said FIG. It is sectional drawing of the decomposition | disassembly state of the said FIG. It is sectional drawing which shows the 3rd modification of an uneven | corrugated fitting structure. It is a principal part expanded sectional view of the uneven | corrugated fitting structure shown in the said FIG. It is sectional drawing of the assembly state of the uneven | corrugated fitting structure shown in the said FIG. It is sectional drawing of the other inner ring | wheel which comprises an uneven | corrugated fitting structure. It is a principal part expanded sectional view of the inner ring | wheel of the constant velocity universal joint shown in the said FIG. It is sectional drawing which shows the modification of a track groove. It is a longitudinal cross-sectional view of the undercut free type constant velocity universal joint which shows 2nd Embodiment of this invention. It is a longitudinal cross-sectional view of the DOJ type constant velocity universal joint which shows 3rd Embodiment of invention. It is sectional drawing which shows the 6th modification of an uneven | corrugated fitting structure. It is a principal part enlarged view of FIG.
Explanation of symbols
3 Ball 4 Cage 5 Shaft 8 Inner spherical surface (inner peripheral surface)
9 Track groove 10 Outer spherical surface (outer peripheral surface)
11 Track groove 22, 79, 93 Shaft hole 35 Convex part 36 Concave part 37 Inner diameter surface 38 Fitting contact part 45 Protruding part 50 Pocket part 52 Gutter part 55 Convex part 66 Outer diameter surface 71 Inner spherical surface (inner peripheral surface)
72 Track groove 72a Back side track groove 74 Outer spherical surface (outer peripheral surface)
75 Track groove 77 Ball 78 Cage 82 Track groove 84 Cylindrical inner peripheral surface 92 Track groove 94 Spherical outer peripheral surface 100 Ball 101 Cage M Concavity and convexity fitting structure

Claims (20)

  1. An outer joint member, an inner joint member inserted into the outer joint member, a torque transmission ball that is interposed between the outer joint member and the inner joint member, and a cage that holds the torque transmission ball. In a constant velocity universal joint,
    At least one of the track groove of the outer joint member or the track groove of the inner joint member is formed by cold forging, and the components including the outer joint member, the inner joint member, the ball and the cage are assembled by random matching. The inner joint member and the shaft that is inserted into the shaft hole of the inner joint member are connected via the concave-convex fitting structure, and either one of the convex portion of the inner joint member or the shaft and the counterpart to be fitted to the convex portion. A constant velocity universal joint characterized in that the entire fitting contact portion with the concave portion of the member is in close contact.
  2. An outer joint member, an inner joint member inserted into the outer joint member, a torque transmission ball that is interposed between the outer joint member and the inner joint member, and a cage that holds the torque transmission ball. In a constant velocity universal joint,
    The outer joint member and the inner joint member are formed so that at least one of the track groove of the outer joint member or the track groove of the inner joint member is formed by cold forging, and the PCD clearance or the like is within a specified range. In addition to selecting and assembling components including a ball and a cage, the inner joint member and the shaft that is inserted into the shaft hole of the inner joint member are connected via a concave-convex fitting structure, and either the inner joint member or the shaft is connected. A constant velocity universal joint characterized in that the entire fitting contact portion between the one convex portion and the concave portion of the mating member fitted to the convex portion is in close contact.
  3.   An outer joint member in which a plurality of track grooves extending in the axial direction are formed on the inner peripheral surface, and an inner side in which a plurality of track grooves extending in the axial direction in pairs with the track grooves of the outer joint member are formed on the outer peripheral surface Between the joint member, a plurality of balls interposed between the track groove of the outer joint member and the track groove of the inner joint member, and between the inner peripheral surface of the outer joint member and the outer peripheral surface of the inner joint member 3. The constant velocity universal joint according to claim 1, wherein the constant velocity universal joint is provided with a cage that holds the ball interposed therebetween, and each track groove has a curved area.
  4.   An outer joint member in which a plurality of track grooves extending in the axial direction are formed on the inner peripheral surface, and an inner side in which a plurality of track grooves extending in the axial direction in pairs with the track grooves of the outer joint member are formed on the outer peripheral surface Between the joint member, a plurality of balls interposed between the track groove of the outer joint member and the track groove of the inner joint member, and between the inner peripheral surface of the outer joint member and the outer peripheral surface of the inner joint member 3. A fixed type in which a cage for holding the ball is provided, and one end of each track groove is in a straight shape parallel to the axis. The constant velocity universal joint described.
  5.   An outer joint member having a plurality of track grooves extending in the axial direction on a cylindrical inner peripheral surface; an inner joint member having a plurality of track grooves extending in the axial direction on a spherical outer peripheral surface; and A plurality of balls which are interposed between the track grooves and the track grooves of the inner joint member and transmit torque; and are interposed between the cylindrical inner peripheral surface of the outer joint member and the spherical outer peripheral surface of the inner joint member. The constant velocity universal joint according to claim 1 or 2, wherein the constant velocity universal joint is a sliding type comprising a cage for holding a ball.
  6.   The PCD clearance of the ball track formed by the track groove of the outer joint member and the track groove of the inner joint member cooperating with the outer joint member is set to -0.02 to +0.3 mm. The constant velocity universal joint described in 1.
  7.   The constant velocity universal joint according to any one of claims 1 to 6, wherein the cross-sectional shape of the track groove of the outer joint member and the track groove of the inner joint member is a Gothic arch shape that makes an angular contact with the ball.
  8.   A convex portion extending in the axial direction provided on one of the outer diameter surface of the shaft and the inner diameter surface of the shaft hole of the inner joint member is press-fitted into the other along the axial direction, and the convex portion is projected on the other. The constant velocity universal joint according to any one of claims 1 to 7, wherein a concave portion that is closely fitted to the portion is formed.
  9.   The shaft is provided with a convex portion, and at least the hardness of the axial end portion of the convex portion is made higher than the inner diameter portion of the inner joint member so that the shaft extends into the axial hole of the inner joint member. 9. The constant velocity universal joint according to claim 8, wherein a concave portion that closely fits to the convex portion is formed on the inner diameter surface of the inner joint member at the convex portion by press-fitting from the portion side.
  10.   A convex portion is provided on the inner diameter surface of the shaft hole of the inner joint member, and at least the hardness of the end portion in the axial direction of the convex portion is made higher than the outer diameter portion of the shaft, and the convex portion on the inner joint member side is 9. The constant velocity universal joint according to claim 8, wherein a concave portion that closely fits to the convex portion is formed on the outer diameter surface of the shaft by press-fitting into the shaft from the direction end portion side.
  11.   The constant velocity universal joint according to claim 9, wherein the shaft is provided with a pocket portion that accommodates a protruding portion generated by forming the concave portion by the press-fitting.
  12.   11. The constant velocity universal joint according to claim 10, wherein a pocket portion for accommodating a protruding portion generated by forming the concave portion by the press-fitting is provided on an inner diameter surface of the shaft hole of the inner joint member.
  13. The pocket portion for storing the protruding portion is provided on the press-fitting start end side of the convex portion of the shaft, and the collar portion for alignment with the shaft hole of the inner joint member is provided on the anti-convex portion side of the pocket portion. The constant velocity universal joint according to claim 11, wherein
  14.   The constant velocity universal joint according to any one of claims 1 to 13, wherein any part in the protruding direction of the convex part corresponds to the position of the concave part forming surface before the concave part is formed.
  15.   The maximum diameter dimension of the arc connecting the vertices of the plurality of protrusions is made larger than the inner diameter dimension of the shaft hole of the inner joint member, and the maximum outer diameter dimension of the shaft outer diameter surface between adjacent protrusions is set to the axis of the inner joint member. The constant velocity universal joint according to claim 14, wherein the constant velocity universal joint is smaller than an inner diameter of the hole.
  16.   The minimum diameter dimension of the arc connecting the vertices of the plurality of convex portions of the shaft hole of the inner joint member is made smaller than the outer diameter size of the inner joint member fitting insertion portion of the shaft, and the inner diameter surface of the shaft hole between the adjacent convex portions 15. The constant velocity universal joint according to claim 14, wherein the minimum inner diameter dimension is larger than the outer diameter dimension of the inner joint member fitting portion of the shaft.
  17.   The circumferential thickness of the projecting direction intermediate portion of the convex portion is smaller than the circumferential dimension at a position corresponding to the intermediate portion between the convex portions adjacent in the circumferential direction. The constant velocity universal joint according to any one of 16.
  18.   The sum of the circumferential thicknesses of the projecting direction intermediate portions of the convex portions is the sum of the circumferential thicknesses at positions corresponding to the intermediate portions of the mating convex portions that fit between the convex portions adjacent in the circumferential direction. The constant velocity universal joint according to claim 1, wherein the constant velocity universal joint is also reduced.
  19.   The constant velocity universal joint according to any one of claims 1 to 18, wherein an uneven portion along the axial direction is provided in at least part of the axial direction on the convex portion side.
  20.   The constant velocity universal joint in any one of Claims 1-19 which formed the uneven | corrugated | grooved part along the axial direction of the said convex part side in the shape of a sawtooth.
JP2007096558A 2007-04-02 2007-04-02 Constant velocity universal joint Pending JP2008256022A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2007096558A JP2008256022A (en) 2007-04-02 2007-04-02 Constant velocity universal joint

Applications Claiming Priority (6)

Application Number Priority Date Filing Date Title
JP2007096558A JP2008256022A (en) 2007-04-02 2007-04-02 Constant velocity universal joint
CN 200880001344 CN101611233B (en) 2007-01-17 2008-01-17 Constant velocity universal joint
US12/522,289 US8506202B2 (en) 2007-01-17 2008-01-17 Constant velocity universal joint
PCT/JP2008/050510 WO2008088007A1 (en) 2007-01-17 2008-01-17 Constant velocity universal joint
KR20097011492A KR101510797B1 (en) 2007-01-17 2008-01-17 constant velocity universal joint
EP08703365.0A EP2119929B1 (en) 2007-01-17 2008-01-17 Constant velocity universal joint

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Publication number Priority date Publication date Assignee Title
WO2010052985A1 (en) * 2008-11-06 2010-05-14 Ntn株式会社 Fixed constant velocity universal joint, method of manufacturing fixed constant velocity universal joint, and bearing device adapted for use in driving wheel and using fixed constant velocity universal joint
WO2010119723A1 (en) * 2009-04-16 2010-10-21 本田技研工業株式会社 Tripod constant velocity joint, and method and device for assembling same
WO2016114050A1 (en) * 2015-01-15 2016-07-21 Ntn株式会社 Constant-velocity universal joint

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JP2003049861A (en) * 2001-08-03 2003-02-21 Ntn Corp Cage of fixed constant velocity universal joint and its manufacturing method and fixed constant velocity universal joint
JP2005188620A (en) * 2003-12-25 2005-07-14 Ntn Corp Stationary type constant velocity universal joint
JP2005193757A (en) * 2004-01-06 2005-07-21 Ntn Corp Bearing apparatus for driving wheel
JP2005337290A (en) * 2004-05-24 2005-12-08 Ntn Corp Drive shaft for all terrain vehicle
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WO2007145019A1 (en) * 2006-06-16 2007-12-21 Ntn Corporation Constant velocity universal joint

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JPS6251694B2 (en) * 1978-06-21 1987-10-31 Hitachi Ltd
JPH0217730B2 (en) * 1984-04-17 1990-04-23 Ntn Toyo Bearing Co Ltd
JPH0229262Y2 (en) * 1986-09-30 1990-08-06
JPH06312322A (en) * 1993-04-26 1994-11-08 Mitsubishi Materials Corp Hollow movable shaft and manufacture thereof
JP2001323920A (en) * 2000-05-18 2001-11-22 Honda Motor Co Ltd Structure for fitting spline shaft for constant velocity joint
JP2002310180A (en) * 2001-04-09 2002-10-23 Ntn Corp Constant velocity universal joint
JP2003049861A (en) * 2001-08-03 2003-02-21 Ntn Corp Cage of fixed constant velocity universal joint and its manufacturing method and fixed constant velocity universal joint
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Publication number Priority date Publication date Assignee Title
WO2010052985A1 (en) * 2008-11-06 2010-05-14 Ntn株式会社 Fixed constant velocity universal joint, method of manufacturing fixed constant velocity universal joint, and bearing device adapted for use in driving wheel and using fixed constant velocity universal joint
JP2010112469A (en) * 2008-11-06 2010-05-20 Ntn Corp Fixed-type constant velocity universal joint, and method of manufacturing the same and driving wheel bearing unit using the same
US8499457B2 (en) 2008-11-06 2013-08-06 Ntn Corporation Fixed constant velocity universal joint, method of manufacturing fixed constant velocity universal joint, and bearing device adapted for use in driving wheel and using fixed constant velocity universal joint
WO2010119723A1 (en) * 2009-04-16 2010-10-21 本田技研工業株式会社 Tripod constant velocity joint, and method and device for assembling same
US8474130B2 (en) 2009-04-16 2013-07-02 Honda Motor Co., Ltd. Tripod constant velocity joint, and method and device for assembling same
WO2016114050A1 (en) * 2015-01-15 2016-07-21 Ntn株式会社 Constant-velocity universal joint
JP2016133127A (en) * 2015-01-15 2016-07-25 Ntn株式会社 Constant velocity universal joint

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