WO2011065400A1 - 固定型等速自在継手 - Google Patents
固定型等速自在継手 Download PDFInfo
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- WO2011065400A1 WO2011065400A1 PCT/JP2010/070985 JP2010070985W WO2011065400A1 WO 2011065400 A1 WO2011065400 A1 WO 2011065400A1 JP 2010070985 W JP2010070985 W JP 2010070985W WO 2011065400 A1 WO2011065400 A1 WO 2011065400A1
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- center
- joint member
- joint
- track groove
- track
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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
- F16D3/2237—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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
- F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
- F16D3/20—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members
- F16D3/22—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts
- F16D3/223—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts
- F16D3/224—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts the groove centre-lines in each coupling part lying on a sphere
- F16D3/2245—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts the groove centre-lines in each coupling part lying on a sphere where the groove centres are offset from the joint centre
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
- F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
- F16D3/20—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members
- F16D3/22—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts
- F16D3/223—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts
- F16D2003/22309—Details of grooves
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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
- F16D2250/00—Manufacturing; Assembly
- F16D2250/0038—Surface treatment
- F16D2250/0053—Hardening
Definitions
- the present invention relates to a fixed type constant velocity universal joint, and in particular, is a type that allows only angular displacement between two connected drive and driven shafts, and is used in power transmission systems of automobiles and various industrial machines.
- the present invention relates to an undercut-free type fixed type constant velocity universal joint including eight torque transmission balls.
- the fixed type constant velocity universal joint includes a Rzeppa type (BJ) (for example, Patent Document 1) and an undercut free type (UJ).
- BJ Rzeppa type
- UJ undercut free type
- the Rzeppa-type fixed type constant velocity universal joint includes an outer joint member 3 in which a plurality of track grooves 2 are formed in the inner spherical surface 1 along the axial direction at equal intervals in the circumferential direction, and the outer spherical surface 4.
- a plurality of track grooves 5 paired with the track grooves 2 of the outer joint member 3 are formed along the axial direction at equal intervals in the circumferential direction, and the track grooves 2 and the inner joint of the outer joint member 3
- maintain is provided.
- a plurality of window portions 9 in which the balls 7 are accommodated are arranged in the cage 8 along the circumferential direction.
- the cage 8 is in spherical contact with the inner spherical surface of the outer joint member 3 and the outer spherical surface of the inner joint member 6.
- the curvature centers (O2, O1) of the ball center locus lines of the track grooves 2 and 5 of the outer joint member 3 and the inner joint member 6 are respectively symmetrical with respect to the joint center Oj.
- the curvature center O1 and the curvature center O2 are offset from the joint center Oj by an equal distance in the opposite direction and offset in the axial direction.
- the track groove 2 of the outer joint member 3 is offset from the joint center Oj by a predetermined distance along the joint center axis X toward the joint opening side, and the track groove 5 of the inner joint member 6 is moved from the joint center Oj to the joint center axis X.
- a predetermined distance is offset along the joint back side.
- the joint center axis X is a straight line including the axis of the outer joint member 3 and the axis of the inner joint member 6 in a state where the joint operating angle is 0 °
- the joint center plane is the center of the torque transmission ball 7.
- a plane that is perpendicular to the joint center axis and the joint center Oj is an intersection of the joint center plane and the joint center axis.
- the torque transmitting ball track formed by the track groove 2 of the outer joint member 3 and the track groove 5 of the inner joint member 6 has a wedge shape that gradually spreads from one to the other in the axial direction.
- Each ball 7 is accommodated in this wedge-shaped torque transmitting ball track, and transmits torque between the outer joint member 3 and the inner joint member 6.
- a cage 8 is incorporated to hold all the balls 7 in the joint plane (plane perpendicular to the bisector of the operating angle).
- the fixed-type constant velocity universal joint of the Rzeppa type has a structure with six torque transmission balls that has been used for many years as a technical standard, and has gained the support of many users in terms of performance and reliability.
- the present applicant has achieved a high-efficiency, drastic light weight and compactness while ensuring strength, load capacity and durability equivalent to or better than the six-ball zeppa joint as the technical standard.
- a single ball zeppa joint has been developed and already proposed (for example, Patent Document 1 below).
- the UJ type fixed type constant velocity universal joint includes an outer joint member 13 in which a plurality of track grooves 12 are formed on the inner diameter surface 11 along the axial direction at equal intervals in the circumferential direction.
- An inner joint member 16 in which a plurality of track grooves 15 paired with the track grooves 12 of the outer joint member 13 are formed on the outer diameter surface 14 along the axial direction at equal intervals in the circumferential direction, and the track of the outer joint member 13
- a plurality of balls 17 that transmit torque between the groove 12 and the track groove 15 of the inner joint member 16, and between the inner diameter surface 11 of the outer joint member 13 and the outer diameter surface 14 of the inner joint member 16.
- a cage 18 for interposing and holding the ball 17.
- a plurality of window portions 19 in which the balls 17 are accommodated are arranged in the cage 18 along the circumferential direction.
- the track groove 12 of the outer joint member 13 has an opening in which the track groove ball center locus line is an arcuate portion and the track groove ball center locus line is a straight portion parallel to the outer joint member axis.
- the back side track groove 12a has its center of curvature O2 shifted from the joint center Oj in the axial direction toward the opening side of the outer joint member 13.
- the track groove 15 of the inner joint member 16 includes an inner track groove 15a in which the track groove ball center locus line is a straight portion parallel to the inner joint member axis, and an opening side in which the track groove ball center locus line is an arc portion. It consists of a track groove 15b.
- the center of curvature O1 of the opening side track groove 15b is provided at an equal distance F away from the joint center Oj in the axial direction on the back side opposite to the center of curvature O2 of the back side track groove 12a of the outer joint member 13.
- the track shape of the outer joint member 13 of the UJ type is undercut-free with the opening side being a straight shape in contrast to the Rzeppa type in which the entire region is an arc shape. For this reason, since the ball position is on the outer diameter side at the opening compared to the BJ type, the interference angle between the shaft (the shaft fitted into the inner joint member) and the track groove 12 of the outer joint member 13 is increased, and the UJ type Has a larger operating angle than the BJ type. Further, since the track shape of the UJ type outer joint member 13 is a straight shape on the opening side, the movement amount of the ball 17 in the radial direction is increased in the outer diameter side direction. In order to hold, the outer diameter of the cage 18 is also increased. From this, the inner spherical surface diameter of the outer joint member 13 is increased.
- the track depth refers to the joint internal force analysis in the rotating state, and from the ball contact point at the position where the contact ellipse of the ball moving in the axial direction and the contact angle direction in the single rotation is closest to the spherical surface. Expressed as the distance to the sphere.
- the UJ type has a larger ball diameter than the Zepper type at the same size, and the pitch circle PCD of the ball, and thus the outer joint member.
- the outer diameter is also increased.
- the UJ type shown in FIG. 18 has a cage offset shape that is effective in securing the outer joint member back side track depth. That is, with respect to the joint center Oj, the center O4 of the outer spherical surface 18a of the cage 18 is offset by fc toward the axial opening side, and the center O3 of the inner spherical surface 18b of the cage 18 is offset by fc toward the rear side in the axial direction. .
- Such a cage offset type is called a track direction cage offset.
- the 8-ball UJ type joint has a ball diameter smaller than that of the 6-ball. Therefore, regardless of the size or number of balls, PCR (the center of the arc of the track groove of the outer joint member or the track groove of the inner joint member).
- the offset amount is set to be small so that the radial dimension (thickness) of the cage corresponding to the radial movement amount determined by the offset amount and the length of the line segment connecting the arc center and the ball center can be secured. As shown in FIG. 14, a cage offset is employed.
- the track groove of the outer joint member includes an opening-side first guide groove centered on the joint center, and a back-side second guide groove centered on a point offset from the joint center to the radially opposite side. It is formed with. Further, the track groove of the inner joint member is further radiused from the center of the back side second track groove centered on the point offset from the joint center to the back side along the joint center axis, and from the center of the back side second guide groove. The opening side second guide groove is centered on a point offset in the opposite direction.
- the depth of the back side first guide groove of the outer joint member is increased, and the thickness of the inner joint member is increased at the opening side second guide groove portion of the inner joint member. Therefore, when the joint takes a high operating angle, the ball does not ride on the back side first guide groove of the outer joint member and the edge portion of the groove is not chipped. The member will not be damaged.
- the center of the track groove of the outer joint member and the center of the track groove of the inner joint member are spaced apart from each other by an equal distance from the diameter direction surface (joint center surface) in the axial direction. Is offset to a position spaced apart by a predetermined amount on the opposite side in the radial direction.
- the center of curvature of the groove center line of the track groove of the outer joint member and the track groove of the inner joint member is decentered on both sides of the joint center surface, and on the plane including the groove center line and the axis. It is set to be on the opposite side beyond the axis. Thereby, the maximum allowable angle of the joint angle can be increased, and the strength is ensured without increasing the outer diameter of the outer joint member.
- Patent Document 5 there is one that can increase the maximum bending angle without affecting the running characteristics. That is, in Patent Document 5, the intersection angle between the tangent to the trajectory curve and the joint rotation axis monotonously increases starting from the point where the distance between the base of the traveling path and the joint rotation axis is the maximum value. It is what you do.
- An object of the present invention is to provide an undercut-free type fixed constant velocity universal joint with eight balls capable of improving the torque capacity at a high operating angle while ensuring durability at a low operating angle. It is to provide.
- the first constant velocity universal joint of the present invention includes an outer joint member in which eight track grooves extending in the axial direction are formed on the inner diameter surface, and an inner joint in which eight track grooves extending in the axial direction are formed on the outer diameter surface. 8 torque transmission ball tracks formed by cooperation of the member, the track groove of the outer joint member and the corresponding track groove of the inner joint member, and 8 pieces arranged on the torque transmission ball track, respectively.
- Torque transmission ball and a cage having a pocket for holding the torque transmission ball, and an undercut free type fixed type having a curved portion and a straight portion on the track groove bottom surface of the outer joint member and the track groove bottom surface of the inner joint member
- a constant velocity universal joint having a joint operating angle of 0 ° and a straight line including the axis of the outer joint member and the axis of the inner member as a joint central axis, the torque transmission
- the center of the track groove of the outer joint member and the center of the track groove of the inner joint member are respectively the joint center when a plane including the center of the rail and perpendicular to the joint center axis is a joint center plane.
- Rt is the distance between the center of the track groove of the outer joint member or the center of the track groove of the inner joint member and the center of the torque transmitting ball, or the center of the track groove of the outer joint member or the inner side.
- the radial offset amount which is the distance from the center of the track groove of the outer joint member or the center of the track groove of the inner joint member, to the joint center axis line.
- the effective hardened layer depth at Hv513 is Di
- the diameter of the ball is When d, a hardened layer having an effective hardened layer depth ratio Di / d of 0.111 or more is formed.
- the second constant velocity universal joint of the present invention includes an outer joint member in which eight track grooves extending in the axial direction are formed on the inner diameter surface, and an inner joint in which eight track grooves extending in the axial direction are formed on the outer diameter surface. 8 torque transmission ball tracks formed by cooperation of the member, the track groove of the outer joint member and the corresponding track groove of the inner joint member, and 8 pieces arranged on the torque transmission ball track, respectively.
- Torque transmission ball and a cage having a pocket for holding the torque transmission ball, and an undercut free type fixed type having a curved portion and a straight portion on the track groove bottom surface of the outer joint member and the track groove bottom surface of the inner joint member
- a constant velocity universal joint having a joint operating angle of 0 ° and a straight line including the axis of the outer joint member and the axis of the inner member as a joint central axis, the torque transmission
- the center of the track groove of the outer joint member and the center of the track groove of the inner joint member are respectively the joint center when a plane including the center of the rail and perpendicular to the joint center axis is a joint center plane.
- the outer spherical center of the cage is offset from the joint central axis to the radial direction opposite to the track grooves from the joint central axis, and the outer spherical center of the cage is the track of the inner joint member. It is arranged on the center side of the groove, and the inner spherical center of the cage is arranged closer to the center side of the track groove of the outer joint member than the joint central plane, and the outer spherical center of the cage or the inner spherical center of the cage and the joint central plane
- fc is the axial distance up to and R is the distance from the center of the torque transmitting ball to the joint center axis
- the distance between the center of the track groove of the outer joint member or the center of the track groove of the inner joint member and the center of the torque transmitting ball is Rt, the center of the track groove of the outer joint member or the track groove of the
- the track depth refers to the joint internal force analysis in the rotating state, and from the ball contact point at the position where the contact ellipse of the ball moving in the axial direction and the contact angle direction in the single rotation is closest to the spherical surface. The distance to the sphere. The greater the distance from the ball contact point to the spherical surface, the better the durability.
- the groove depth of the inner side of the joint of the track groove is relatively less than when no radial offset is provided. Become bigger. For this reason, the rigidity of the joint groove side wall of the track groove increases, so that the joint takes a high operating angle, and the torque is transmitted when the torque transmission ball is close to the joint groove deep side of the track groove. Deformation of the edge portion of the side wall of the groove at the back of the joint is suppressed, and the torsional strength of the joint at a high operating angle region is improved.
- the torque capacity in the high operating angle region is increased, and the edge load at the side wall of the joint in the track groove is reduced. As a result, the durability of the joint in the high operating angle region is improved.
- the torque capacity is when the end of the contact ellipse of the contact portion between the torque transmission ball and the track groove overlaps the edge line of the track groove when transmitting torque while taking a certain operating angle. Torque.
- the bottom surface (groove inner surface) of the track groove of the inner joint member has at least an effective hardened layer depth ratio Di / d of 0.111 when the effective hardened layer depth at Hv513 is Di and the ball diameter is d. Since it has the above, the rigidity of the edge part of the track shoulder part of an inner joint member becomes high, and the intensity
- the cage has an effective hardened layer depth at Hv600 of Dc, and when the ball diameter is d, at least the effective hardened layer depth ratio Dc / d is 0.067 or more and the non-ground surface is more hard than the ground surface hardness. However, it is preferable not to have a soft softening layer. By configuring in this way, a high-strength cage can be configured.
- the cut portion is preferably formed by cold forging.
- the outer joint member includes a mouth portion in which the track groove is formed, and a chamfer for allowing an operating angle that expands toward the opening side is formed at an opening end portion of the mouth portion, and the groove of the chamfer and the track groove is formed.
- the constant velocity universal joint is used for connecting a drive shaft of an automobile, for example.
- the torque capacity on the inner side of the outer joint member increases at a high operating angle
- the rigidity of the track groove wall surface is improved, the deformation of the track edge portion is suppressed, and the torsional strength is improved.
- the track depth on the back side of the outer joint member increases at a high operating angle, the riding torque is improved, the edge load is reduced, and the durability at a high operating angle is improved.
- the track depth can be secured as usual, and the durability is equal to or higher than the conventional one.
- the durability is improved.
- the fixed type constant velocity universal joint can be applied to high durability requirements, so that the size can be reduced, the weight can be reduced, and the cost can be reduced.
- the inner joint member has an effective hardened layer depth at Hv513 of Di and a ball diameter of d
- the inner hardened member has at least an effective hardened layer depth ratio Di / d of 0.111 or more.
- the rigidity of the edge part of the track shoulder part of a joint member can be improved, local deformation is suppressed, and strength and durability are improved.
- the contact surface that holds the outer spherical surface of the cage can be enlarged toward the opening side, and the cage can be deformed at high load. Can be suppressed. For this reason, the torsional fatigue strength or quasi-static torsional strength at a high operating angle can be improved as a whole joint.
- the fixed type constant velocity universal joint according to the present invention can improve the strength as a joint and provide a compact one. For this reason, it becomes a fixed type constant velocity universal joint optimal for a drive shaft.
- the fixed type constant velocity universal joint of this embodiment is arranged on the fixed side (wheel side) of a drive shaft of an automobile, for example.
- the inner joint member 36 formed along the axial direction at equal intervals in the circumferential direction and the track groove 32 of the outer joint member 33 and the track groove 35 of the inner joint member 36 are formed in cooperation.
- the cage 38 is provided with a plurality of window portions 39 in which the balls 37 are accommodated along the circumferential direction.
- a tooth mold (serration or spline) 36 a for connecting the shaft portion to the inner diameter surface of the inner joint member 36 is formed.
- the outer joint member 33 includes a mouth portion 33a having the track groove 32 and a shaft portion 33b protruding from the bottom wall of the mouth portion 33a.
- the track groove 32 of the mouse portion 33a includes an inner track groove 32a in which the track groove ball center locus line is a curved portion (arc portion), and an opening in which the track groove ball center locus line is a straight portion parallel to the outer joint member axis. It consists of a side track groove 32b.
- the track groove 35 of the inner joint member 36 includes a back-side track groove 35a in which the track groove ball center locus line is a straight portion parallel to the inner joint member axis, and a track groove ball center locus line is a curved portion (arc portion). And an opening-side track groove 35b.
- the track groove 32 of the outer joint member 33 and the track groove 35 of the inner joint member 36 have a Gothic arch shape formed only by forging, or by shaving after forging.
- the track grooves 32, 35 and the ball 37 are in an angular contact by using a Gothic arch shape. That is, the ball 37 is in contact with the track groove 32 of the outer joint member 33 at two points C11 and C12, and is in contact with the track groove 35 of the inner joint member 36 at two points C21 and C22.
- An angle formed by contact points C11, C12, C21, and C22 between the center Ob of the ball 37 and the track grooves 32 and 35 with respect to the line segment P1 passing through the center Ob of the ball 37 and the joint center Oj is a contact angle ⁇ .
- FIG. 1 and 2 show a state in which the operating angle ⁇ of the joint is 0 °.
- the axis of the outer joint member 33 and the axis of the inner joint member 36 coincide on the straight line X
- the plane P including the center Ob of all the torque transmission balls 37 is orthogonal to the straight line X.
- the straight line X is referred to as a joint center axis X
- the plane P is referred to as a joint center plane P
- the intersection of the joint center plane P and the joint center axis X is referred to as a joint center Oj.
- the center (curvature center) O2 of the inner side track groove 32a of the track groove 32 of the outer joint member 33 is an axial distance F from the joint center plane P to the joint opening side (right side in FIG. 2). They are spaced apart and offset from the joint center axis X to a position separated from the track groove 32 by a radial distance fr on the opposite side in the radial direction. Further, the center O1 of the opening side track groove 35b of the track groove 35 of the inner joint member 36 is separated from the joint center plane P by the axial distance F from the joint back side (left side in the figure), and the joint center axis The track groove 35 is offset from X by a radial distance fr on the opposite side in the radial direction.
- the axial distance (F) between the centers O2, O1 of the track grooves 32, 35 and the joint center plane P is defined as the axial offset amount F
- the radial distance (fr) between the curvature centers O2, O1 and the joint center axis X is referred to as a radial offset amount fr.
- the track groove 32 of the outer joint member 33 and the track groove 35 of the inner joint member 36 have the same axial offset amount F and the same radial offset amount fr.
- the center O4 of the outer spherical surface 38a of the cage 38 and the center O3 of the inner spherical surface 38b of the cage 38 are both on the joint center Oj.
- the radial offset amount which is the distance between the center (curvature center) O2 of the track groove 32 of the outer joint member 33 or the center (curvature center) O1 of the track groove 35 of the inner joint member 36 and the joint center axis X, is fr.
- hardened layers S ⁇ b> 2 and S ⁇ b> 1 are provided on the inner diameter surface 31 of the mouth portion 33 a of the outer joint member 33 or the groove bottom 41 of the track groove 32.
- the outer joint member 33 is made of, for example, carbon steel having a carbon content of 0.46 to 0.58 mass%, and is cold forged at least once, so that the hardness on the outer peripheral side of the mouse portion 27 (other than the hardened layer) Hardness) is Hv (Vickers hardness) 280 or more and 400 or less, and the hardness of the cured layer is Hv 500 or more and 780 or less.
- Induction hardening is a hardening method that applies the principle of heating a conductive object by placing a portion necessary for hardening in a coil through which high-frequency current flows and generating Joule heat by electromagnetic induction.
- Carburizing and quenching is a method in which carbon is infiltrated / diffused from the surface of a low carbon material and then quenched.
- a chamfer 40 for allowing an operating angle that increases in diameter toward the opening side is formed at the opening end of the mouse portion 33a.
- or this opening end surface 42 is made into the non-hardened layer 44 which has not performed the hardening process.
- hardened layers S4 and S3 are provided on the outer diameter surface 34 of the inner joint member 36 or the groove bottom 45 of the track groove 35.
- the inner joint member 36 can be made of, for example, SCr420, and the hardened layers S3 and S4 in this case are at least when the effective hardened layer depth at Hv513 is Di and the ball diameter is d.
- the effective hardened layer depth ratio Di / d is 0.111 or more.
- the effective hardened layer depth refers to the distance from the surface of the hardened layer to the position of the specified limit hardness.
- the limited field hardness defined in this case is Hv513, and when the dimension from the surface of the hardened layer to this hardness is Di and the ball diameter is d, at least Di / d is 0.111. That is, it has a cured layer.
- Various heat treatments such as induction hardening and carburizing and quenching can be employed for forming the hardened layers S3 and S4.
- the upper limit of the effective hardened layer depth can be arbitrarily set within a range in which the strength of the mouse does not decrease based on the thickness of the mouse part 33a of the outer joint member 33, the hardness of the non-hardened part, or the like.
- the cage insertion cut portions 50 are provided in at least two places that are symmetrical with respect to the axis.
- the cut portion 50 is cut out in a flat shape, and the dimension D between the cut portions 50 provided at a 180 ° symmetrical position with respect to the axial center is defined as a pocket of the cage 38 provided at a 180 ° symmetrical position with respect to the axial center. It is set slightly smaller than the inter-dimension D1. Further, the dimension E between adjacent track grooves along the circumferential direction of the outer joint member 33 is set smaller than the pocket axial dimension H of the pocket of the cage 38.
- the cage 38 can be fitted into the outer joint member 33 in a state where the pockets of the cage 38 provided at 180 ° symmetrical positions with respect to the axial center correspond to the cut portions 50. Yes.
- the effective hardened layer depth at Hv600 is Dc, and when the ball diameter is d, at least the effective hardened layer depth ratio Dc / d is 0.067 or more, and the surface of the grinding part is not ground. It shall not have a softening layer softer than the hardness.
- the cage 38 is made of, for example, S48C, and is subjected to thermosetting using, for example, a quenching furnace.
- FIG. 7 and FIG. 8 show a second embodiment of the present invention.
- the outer spherical surface center O4 of the cage 38 is disposed closer to the track groove center O1 side of the inner joint member 36 than the joint center Oj, and the inner spherical surface center O3 of the cage 38 is located outside the joint center Oj.
- the joint member 33 is disposed on the center O2 side of the track groove. That is, the outer spherical surface center O4 of the cage 38 and the inner spherical surface center O3 of the cage 38 are offset from the joint center Oj by fc in the axial direction.
- Such a cage offset type is called an anti-track direction cage offset in opposition to the track direction cage offset of FIG.
- the center (curvature center) O2 of the inner side track groove 32a of the track groove 32 of the outer joint member 33 is separated from the joint center plane P by the axial distance F from the joint opening side.
- the center O1 of the opening side track groove 35b of the track groove 35 of the inner joint member 36 is separated from the joint center plane P by the axial distance F from the joint back side, and the track groove 35 from the joint center axis X. Is offset to a position separated by a radial distance fr on the opposite side in the radial direction.
- the axial distance between the outer spherical surface center O4 of the cage 38 (center of the inner surface of the outer joint member 33) or the inner spherical surface center O3 of the cage 38 (center of the outer surface of the inner joint member 36) and the joint center surface P is fc.
- the outer joint member 33 is provided with hardened layers S2 and S1 on the inner diameter surface 31 of the mouth portion 33a or the groove bottom 41 of the track groove 32.
- Hardened layers S4 and S3 are provided on the outer diameter surface 34 or the track groove 35 of the inner joint member 36.
- the inner joint member 36 can be made of, for example, SCr420, and the hardened layers S3 and S4 in this case are at least when the effective hardened layer depth at Hv513 is Di and the ball diameter is d.
- the structure offset in the radial direction has good operability up to an offset amount smaller than that of the conventional product.
- the amount of deviation from the joint center Oj of the inner joint member 36 mainly caused by the gap is smaller than that of the conventional product.
- the track groove in which eight track loads are generated in the state where the operating angle is taken is caused by the fact that the track groove is positioned radially outward from the joint center axis X as compared with the conventional product.
- the position and amount of displacement of the inner joint member 36 differ depending on the difference in the positional relationship of the balls supporting the inner joint member 36.
- the shaft is bent in the operating angle direction from the operating angle of ⁇ 20 ° to + 20 ° with no torsional torque. That is, the bending resistance torque value in the working angle direction when bent was calculated by mechanism analysis.
- the clearance between the ball 37 and the track groove 35 of the inner joint member 36 and between the ball 37 and the track groove 32 of the outer joint member 33 is usually mass-produced in this type of fixed type constant velocity universal joint. It was a gap of what is. Note that the inner spherical surface (inner diameter surface) 31 of the outer joint member 33 and the outer spherical surface gap of the cage are the small gaps within the set range, and the outer spherical surface (outer diameter surface) 34 of the inner joint member 36 and the cage inner spherical surface 38b This gap was the larger gap within the set range.
- the gap between the window portion 39 of the cage 38 and the ball 37 is also set as a negative gap on the smaller side within the setting range of the gap. That is, the bending resistance torque value in the operating angle direction is likely to be generated and the operability is deteriorated.
- FIG. 10 shows the analysis result of eight balls having a conventional structure not offset in the radial direction (cage offset in the track center direction).
- the thin line indicates the case where R1 is 0.0701
- the thick line indicates the case where R1 is 0.0771
- the middle line indicates the case where R1 is 0.0867.
- FIG. 11 shows the result of comparing the R1 value for the product of the present invention under the same gap condition and comparing the maximum torque value with the conventional product from the analysis for the R1 value.
- the solid line indicates a conventional product (track groove that is not offset in the radial direction and has a cage offset shape), and the alternate long and short dash line indicates the product of the present invention (referred to as product A of the present invention) shown in FIG.
- the broken line indicates the product of the present invention (referred to as product B of the present invention) shown in FIG.
- the structure offset in the radial direction as the product of the present invention has good operability up to an offset amount smaller than that of the conventional product.
- the developed product has a smaller amount of deviation from the joint center of the inner joint member, which is mainly generated by the gap, than the conventional product.
- the position of the track where eight track loads are generated in the state where the operating angle is taken is based on the fact that the track is positioned radially outward from the center axis.
- the product is different from the developed product. That is, this is because the direction and amount of displacement of the inner joint member differ depending on the positional relationship of the balls supporting the inner joint member.
- the operability can be ensured in such a small offset range is a phenomenon peculiar to the undercut free type structure, and the durability at the normal angle has been improved by utilizing this peculiar phenomenon.
- FIG. 12 and FIG. 13 show the track depth values of the outer joint member 33 under the durability test conditions at the normal angle (6 °).
- FIG. 12 shows the relationship between R1 and the track depth of the outer joint member 33.
- FIG. 13 shows the relationship between R3 and the track depth of the outer joint member 33.
- the track depth is a ball that moves in the axial direction and the contact angle ⁇ direction in the track during one rotation by analyzing the internal force of the joint in a rotating state under a normal condition of a large torque (operating angle 6 °).
- the distance L from the ball contact point to the spherical surface at the position where the contact ellipse 51 is closest to the spherical surface see FIG. 3).
- the ball contact ellipse 51 becomes large due to a large load on the track, and the contact ellipse 51 protrudes from the inner diameter surface of the outer joint member 33 to cause separation from the edge load.
- the longer the distance L from the ball contact point to the spherical surface portion the better the durability.
- FIG. 14 shows the PV value of the outer joint member from the analysis result under the normal angle (6 °) durability test condition.
- the PV value is obtained by multiplying the sliding speed between the ball and the track and the track load. The smaller the PV value, the better the durability. From the analysis results, the smaller the R1 value, the smaller the PV value. However, when the R1 value is 0.071 or less, the decrease in the PV value slows down.
- the B type (cage offset product) is advantageous because a small R1 value can be obtained.
- the PV value of the inner joint member has a relationship that increases in reverse to the outer joint member by decreasing the R1 value. For this reason, there is a concern that the durability of the inner joint member may decrease due to an increase in the PV value of the inner joint member.
- each of the ⁇ , ⁇ , ⁇ , ⁇ , ⁇ , and ⁇ invented products in FIG. 14 indicate fixed type constant velocity universal joints of the same type as the ⁇ , ⁇ , ⁇ , ⁇ , and ⁇ shown in FIG. Yes.
- FIG. 15 shows the track depth from the analysis result when a torque of 250 Nm is applied at an operating angle of 46 °.
- the depth is the same as the conventional depth.
- the A type is 0.061 to 0.087
- the B type is 0.044 to 0.087.
- the lower bound value in this case is the limit value of operability, as can be seen from FIG.
- the upper limit is a range in which a normal angle durability test result and a track depth, which will be described later, can be secured more than the conventional products.
- 0.061 to 0.071 for the A type and 0.044 to 0.071 for the B type are more preferable ranges. This is a range in which the PV value is below the conventional product from FIG. By setting the upper limit range, the track depth is further increased and the durability is further improved.
- R2 is preferably 0.01 or less. This is because if R2 exceeds 0.01, the wall thickness on the opening side (joint opening side) of the cage 38 becomes thin, and the strength may decrease.
- the joint back side portion of the track groove 32 is provided.
- the groove depth becomes relatively large. Therefore, when the rigidity of the joint back side wall portion of the track groove 32 is increased, the joint takes a high operating angle, and the torque transmission ball 37 transmits torque at a position close to the joint back side of the track groove 32.
- the deformation of the edge portion of the joint back side wall portion of the track groove 32 is suppressed, and the torsional strength of the joint in the high operating angle region is improved.
- the torque capacity in the high operating angle region increases.
- the torque capacity means that the end of the contact ellipse of the contact portion between the torque transmission ball 37 and the track groove 32 is the edge line of the track groove 32 when transmitting torque while taking a certain operating angle. Overlapping torque.
- the torque capacity on the inner side of the outer joint member increases at a high operating angle
- the rigidity of the track groove wall surface is improved, the deformation of the track edge portion is suppressed, and the torsional strength is improved.
- the track depth on the back side of the outer joint member increases at a high operating angle
- the riding torque is improved, the edge load is reduced, and the durability at a high operating angle is improved.
- the track depth on the back side of the outer joint member 33 was increased by setting the range of R1, R2, and R3.
- the inner joint member 36 has a UJ track shape, the shallow side of the track depth at the high angle is a straight shape, so the inner ring track 35 (the inner joint track at the high angle is used even in the shape of R1, R2, R3.
- the depth of the track 35) of the member 36 is not deep. Therefore, in order to improve the durability and strength of the inner joint member 36 at a high angle, attention was paid to the effective hardened layer depth, and the range of the effective hardened layer depth effective in strength and durability was confirmed by a test.
- the effective hardened layer depth at Hv513 is represented by Di
- the effective hardened layer depth is represented by the effective hardened layer depth ratio Di / d where the diameter of the ball 37 is d.
- Di / d is used as an index of the effective hardened layer depth.
- the reason why Di / d is used as an index of the effective hardened layer depth is as follows. As the joint size increases, the allowable torque increases and the ball diameter also increases. When an allowable torque is applied, the maximum stress is generated at a certain depth from the contact surface due to the contact force of the track from the ball. The depth position where the maximum stress is generated when the allowable torque is applied for each joint size is deeper in proportion to the size, and is also proportional to the ball diameter to be used at the same time.
- the effective hardened layer depth is determined in proportion to the depth from the contact surface where this maximum stress occurs, it is expressed as a ratio divided by the ball diameter as an index indicating the effective hardened layer depth regardless of the joint size.
- the effective hardening depth of the cage was expressed as a ratio divided by the ball diameter proportional to the size and the allowable torque as an index representing the effective hardening layer depth regardless of the joint size.
- the inner joint member 36 has an effective hardened layer depth ratio Di / d of 0.111 or more when the effective hardened layer depth at Hv513 is Di and the ball diameter is d. Therefore, the rigidity of the edge portion of the shoulder portion of the track groove is improved, local deformation is suppressed, and the strength and durability are improved. As described above, by using SCr420 as the inner joint member 36, the forgeability is better than that of the SCr435 and the cost can be reduced. Further, the core hardness can be changed from Hv300 to Hv400. If it is less than Hv300, the required strength cannot be obtained, and if it is Hv400 or more, cracks are likely to occur and the improvement in strength is suppressed.
- the cage 38 when the effective hardened layer depth at Hv600 is Dc and the ball diameter is d, at least the effective hardened layer depth ratio Dc / d is 0.067 or more and the hardened surface of the grinding part is not ground. Since the softening layer is softer than the above, a high-strength cage can be configured. Moreover, since a quenching furnace is used, cost reduction can be achieved compared with induction hardening.
- the cage insertion cut portions (relief portions) 50 are provided in two symmetrical positions with respect to the axial center at the opening end of the inner diameter surface 31 of the outer joint member 33, the spherical area on the opening side of other portions is large. Thus, the strength and durability are improved.
- the shape of the two relief portions 50 is a planar shape and is along the window frame shape of the cage 38, and the spherical area of the central portion in the circumferential direction of the inner sphere is larger than the arc shape by the conventional turning. Larger and more desirable. Further, if the two relief portions are formed by cold forging, it can be realized at a low cost.
- the cup portion (mouse portion) of the outer joint member 33 is maintained in a state where the maximum operating angle is maintained and the radial dimension is not increased.
- 33 can be increased in volume.
- the outer peripheral surface of the opening end surface 42 in the protruding portion 43 and the cup portion (mouse portion) 33a continuous to the opening end surface 42 has the non-hardening layer 44, the non-hardening layer 44 on the opening end side increases. Deformation due to induction hardening on the opening end side is suppressed, yield is increased, and cost reduction can be achieved.
- the present invention has been described.
- the present invention is not limited to the above-described embodiment, and various modifications are possible.
- the axial offset amount, the radial offset amount, the cage offset amount, etc. , R1, R2, and R3 can be arbitrarily set within a range where the optimum values are obtained.
- the R1 value can be set low by improving the operability due to the radial offset, the outer spherical surface center O4 of the cage 38 is disposed closer to the center O2 side of the track groove 32 of the outer joint member 33 than the joint center Oj.
- the inner spherical surface center O3 of 38 may be disposed closer to the center O1 side of the track groove 35 of the inner joint member 36 than the joint center Oj.
- the fixed type constant velocity universal joint according to the present invention is not limited to a drive shaft, but can be used for a propeller shaft and a power transmission system of various other industrial machines.
- the curved portions of the track grooves 32 and 35 have a single circular arc. You may form with a circular arc. If the curved portion is a single circular arc, there are advantages that the processing is easy and the manufacturing cost is low.
- Example 1 (In this Example 1 and Example 2 described later, the outer joint member is called an outer ring and the inner joint member is called an inner ring) A service angle (operating angle 6 °) durability test under a large torque condition was performed, and the results are shown in Table 2 below.
- two samples of conventional products (conventional product No. 1, conventional product No. 2, 2) are manufactured, and two samples of the invention product A1 (invention product A1 No. 1, 1, product A1 No. 2) are manufactured.
- 4 samples of invention product A2 and invention product B (invention product A2No, 1, invention product A2No, 2, invention product A2No, 3, invention product A2No, 4, invention product B1No, 1, invention product B1No, 2.
- the durability test was performed under the conditions of a torque of 834 Nm and a rotation speed of 230 r / min.
- the conventional product has a defect from the inner ring, but the inventive product has no problem with the inner ring. This is because the track main curvature is large because the radius of the arc of the inner ring is large due to the offset in the radial direction, thereby reducing the surface pressure.
- the analysis results of the track depth and PV Similarly, it has been confirmed that the defects occurring in the outer ring are more durable as the track depth is deeper and the PV value is lower. It can be seen that the invention product is better in durability than the conventional product.
- Example 2 Next, a durability test at a high angle was performed, and the results are shown in Table 3 below.
- two samples of the conventional product (conventional product No. 1, conventional product No. 2) are manufactured, and two samples of the inventive product A1, the inventive product A2, and the inventive product B (the inventive product A1 No. 1, Invention A1No.2, Invention A2No.1, Invention A2No.2, Invention B1No.1, Invention B1No.2)
- the durability test was performed under the conditions of a torque of 549 Nm, an angle of 0 to 46 ° (swing), and a rotational speed of 80 r / min.
- the conventional products in Table 3 used in the high-angle endurance test have the conventional specifications in Table 4, and the inventive products A1, A2, and B1 in Table 3 have the inner rings as the specifications (a) in Table 4 below.
- the specifications of (c) in Table 4 were used for each outer ring, and the specifications of (b) in Table 4 were used for the cage.
- Example 3 Next, a rotational torsion strength test was conducted. In this test, the operating angle was set at 46 °, and the torque was gradually increased until it was damaged in a state where it was rotated at a constant low speed. The strength was evaluated based on the torque value at the time of failure. The results are shown in the graph of FIG.
- the inner ring is replaced with the invention specification (a) in Table 4
- the cage is replaced with the invention specification (b) in Table 4
- the outer ring is replaced with the invention specification (c) in Table 4
- the inner ring, the cage and the outer ring are replaced with the invention specifications of (a), (b) and (c), respectively, ), (B), (c), and (d) were replaced with the invention specifications.
- FIG. 19 shows the relationship between the hardened layer depth ratio Di / d of the inner ring and the breakage torque, as a result of the rotational torsional strength test for each test product with respect to the invention specification (a).
- the breakage torque is shown as a ratio to the conventional product average breakage torque of the conventional specification.
- the conventional specification has a variation in Di / d of 0.075 and the failure torque ratio within ⁇ 1% to + 2.1%.
- the invention specification has a Di / d of 0.108 to 0.109 and a failure torque ratio. Is + 2.1% to + 5.2%, and the failure torque ratio of Di / d of 0.185 is improved by + 6.5% to + 7.9%. From these, if Di / d is 0.108 or more, the strength is improved as compared with the conventional specification, but more desirably 0.111 or more can ensure sufficient strength improvement.
- FIG. 20 shows the relationship between the breakage torque and the inner ring spherical surface bulge amount ( ⁇ ) (see FIG. 21) for the test product.
- ⁇ the inner ring spherical surface bulge amount
- the inner ring of the invention specification with Di / d of 0.108 to 0.109 had a larger ⁇ amount when the breaking torque was larger. Therefore, the cage fractured due to the rise of the spherical surface of the inner ring and the strength of the cage itself. In this way, it can be confirmed that the strength of the inner ring is improved by the invention specification, and the strength is improved by suppressing the decrease in strength due to the rise.
- This is a fixed type constant velocity universal joint that only allows angular displacement between the two axes of the connected drive side and driven side. It is an undercut free type having a curved portion and a straight portion on the track groove bottom surface of the outer joint member and the track groove bottom surface of the inner joint member. It can be used for power transmission systems of drive shafts, propeller shafts, and various other industrial machines.
Abstract
Description
大きなトルク条件での常用角(作動角6°)耐久試験を行って、その結果を次の表2に表した。この場合、従来品のサンプルを2個(従来品No,1、従来品No,2)製作し、前記発明品A1のサンプルを2個(発明品A1No,1、発明品A1No,2)製作し、前記発明品A2及び発明品Bのサンプルをそれぞれ4個(発明品A2No,1、発明品A2No,2、発明品A2No,3、発明品A2No,4、発明品B1No,1、発明品B1No,2、発明品B1No,3、発明品B1No,4)製作した。トルク834Nm、回転速度230r/minの条件で耐久試験を行なった。
次に高角での耐久試験を行い、その結果を次の表3に表した。この場合、従来品のサンプルを2個(従来品No.1、従来品No.2)製作し、発明品A1、発明品A2、及び発明品Bのサンプルを2個(発明品A1No.1、発明品A1No.2、発明品A2No.1、発明品A2No.2発明品B1No.1、発明品B1No.2)製作した。トルク549Nm、角度0~46°(揺動)、回転速度80r/minの条件で耐久試験を行った。
次に回転捩り強度試験を行った。この試験は、作動角を46°とり、低速一定回転させた状態で、破損するまでトルクを次第に増加させていき、破損時トルク値により強度を評価した。その結果を図16のグラフ図と次の表5に示した。従来品において、内輪を表4の発明仕様(a)に代えたもの、ケージを表4の発明仕様(b)に代えたもの、外輪を前記表4の発明仕様(c)に代えたもの、外輪を表4の発明仕様(d)に代えたもの、内輪とケージと外輪とをそれぞれ(a)、(b)、及び(c)の発明仕様に代えたもの、発明品B1において、(a)、(b)、(c)、及び(d)の発明仕様に代えたものについて試験を行った。
32,35 トラック溝
33a マウス部
34 外径面
37 トルク伝達ボール
38 ケージ
40 チャンファ
42 開口端面
44 非硬化層
45 溝底
Claims (9)
- 内径面に軸方向に延びる8本のトラック溝を形成した外側継手部材と、外径面に軸方向に延びる8本のトラック溝を形成した内側継手部材と、外側継手部材のトラック溝とこれに対応する内側継手部材のトラック溝とが協働して形成される8本のトルク伝達ボールトラックと、該トルク伝達ボールトラックにそれぞれ配された8個のトルク伝達ボールと、トルク伝達ボールを保持するポケットを有するケージとを備え、外側継手部材のトラック溝底面及び内側継手部材のトラック溝底面に曲線部とストレート部を有するアンダーカットフリータイプの固定型等速自在継手であって、
継手の作動角が0°の状態で、前記外側継手部材の軸線と前記内側部材の軸線とを含む直線を継手中心軸線、前記トルク伝達ボールの中心を含み、前記継手中心軸線と直交する平面を継手中心面としたとき、
前記外側継手部材のトラック溝の中心と前記内側継手部材のトラック溝の中心とが、それぞれ、前記継手中心面から軸方向両側に離間し、かつ、前記継手中心軸線からこれらトラック溝に対して半径方向反対側に離間した位置にオフセットされているとともに、前記ケージの外球面中心とケージの内球面中心とを一致させ、
前記外側継手部材のトラック溝の中心又は前記内側継手部材のトラック溝の中心と前記トルク伝達ボールの中心との間の距離をRt、前記外側継手部材のトラック溝の中心又は前記内側継手部材のトラック溝の中心と前記継手中心面との間の軸方向距離をFとしたとき、FとRtとの比R1(=F/Rt)が0.061≦R1≦0.087であり、かつ、前記外側継手部材のトラック溝の中心又は前記内側継手部材のトラック溝の中心と前記継手中心軸線までの距離である半径方向オフセット量をfrとしたとき、frと前記Rtとの比R3(=fr/Rt)が0.07≦R3≦0.19であり、さらに、内側継手部材のトラック溝の底面には、Hv513での有効硬化層深さをDiとし、ボールの直径をdとしたときに、少なくとも有効硬化層深さ比Di/dが0.111以上となる硬化層が形成されていることを特徴とする固定型等速自在継手。 - 内径面に軸方向に延びる8本のトラック溝を形成した外側継手部材と、外径面に軸方向に延びる8本のトラック溝を形成した内側継手部材と、外側継手部材のトラック溝とこれに対応する内側継手部材のトラック溝とが協働して形成される8本のトルク伝達ボールトラックと、該トルク伝達ボールトラックにそれぞれ配された8個のトルク伝達ボールと、トルク伝達ボールを保持するポケットを有するケージとを備え、外側継手部材のトラック溝底面及び内側継手部材のトラック溝底面に曲線部とストレート部を有するアンダーカットフリータイプの固定型等速自在継手であって、
継手の作動角が0°の状態で、前記外側継手部材の軸線と前記内側部材の軸線とを含む直線を継手中心軸線、前記トルク伝達ボールの中心を含み、前記継手中心軸線と直交する平面を継手中心面としたとき、
前記外側継手部材のトラック溝の中心と前記内側継手部材のトラック溝の中心とが、それぞれ、前記継手中心面から軸方向両側に離間し、かつ、前記継手中心軸線からこれらトラック溝に対して半径方向反対側に離間した位置にオフセットされ、
ケージの外球面中心が継手中心面よりも内側継手部材のトラック溝の中心側に配置されるとともに、ケージの内球面中心が継手中心面よりも外側継手部材のトラック溝の中心側に配置されて、ケージの外球面中心又はケージの内球面中心と継手中心面までの軸方向距離をfcとし、トルク伝達ボールの中心から継手中心軸線までの距離をRとしたとき、fcとRとの比R2(=fc/R)が0.01以下であり、
前記外側継手部材のトラック溝の中心又は前記内側継手部材のトラック溝の中心と前記トルク伝達ボールの中心との間の距離をRt、前記外側継手部材のトラック溝の中心又は前記内側継手部材のトラック溝の中心と前記継手中心面との間の軸方向距離をFとしたとき、FとRtとの比R1(=F/Rt)が0.044≦R1≦0.087であり、かつ、前記外側継手部材のトラック溝の中心又は前記内側継手部材のトラック溝の中心と前記継手中心軸線までの距離である半径方向オフセット量をfrとしたとき、frと前記Rtとの比R3(=fr/Rt)が0.07≦R3≦0.19であり、さらに、内側継手部材のトラック溝の底面には、Hv513での有効硬化層深さをDiとし、ボールの直径をdとしたときに、少なくとも有効硬化層深さ比Di/dが0.111以上となる硬化層が形成されていることを特徴とする固定型等速自在継手。 - FとRtとの比R1(=F/Rt)を0.071以下としたことを特徴とする請求項1又は請求項2に記載の固定型等速自在継手。
- frとRtとの比R3(=fr/Rt)を0.15以上としたことを特徴とする請求項1~請求項3のいずれか1項に記載の固定型等速自在継手。
- ケージは、Hv600での有効硬化層深さをDcとし、ボールの直径をdとしたときに少なくとも有効硬化層深さ比Dc/dが0.067以上で非研削表面に研削部表面の硬さよりも軟らかい軟化層を有さないことを特徴とする請求項1~請求項4のいずれか1項に記載の固定型等速自在継手。
- 前記外側継手部材の内径面の開口端に、ケージ挿入用のカット部を軸心に関して対称となる少なくとも2箇所に設けたことを特徴とする請求項1~請求項5のいずれか1項に記載の固定型等速自在継手。
- 前記カット部を冷間鍛造にて成形したことを特徴とする請求項6に記載の固定型等速自在継手。
- 前記外側継手部材は前記トラック溝が形成されたマウス部を備え、このマウス部の開口端部に開口側に向かって拡径する作動角許容用のチャンファを形成し、このチャンファとトラック溝の溝底との交点からのマウス部の開口端部の突出量をtとし、ボールの直径をdとしたときに、t=0.13d~0.185dとの関係を満たすとともに、マウス部の開口端面乃至この開口端面に連続するマウス部の外周面を、硬化処理を施していない非硬化層を有することを特徴とする請求項1~請求項7のいずれか1項に記載の固定型等速自在継手。
- 自動車のドライブシャフトの連結に用いられる請求項1~請求項8のいずれか1項に記載の固定型等速自在継手。
Priority Applications (3)
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US13/505,763 US8684849B2 (en) | 2009-11-26 | 2010-11-25 | Fixed type constant velocity universal joint |
EP10833246.1A EP2505863B1 (en) | 2009-11-26 | 2010-11-25 | Fixed type constant velocity universal joint |
CN201080053480.8A CN102667202B (zh) | 2009-11-26 | 2010-11-25 | 固定型等速万向接头 |
Applications Claiming Priority (4)
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JP2009-268907 | 2009-11-26 | ||
JP2009268907 | 2009-11-26 | ||
JP2010-261532 | 2010-11-24 | ||
JP2010261532A JP2011133107A (ja) | 2009-11-26 | 2010-11-24 | 固定型等速自在継手 |
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WO2011065400A1 true WO2011065400A1 (ja) | 2011-06-03 |
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US (1) | US8684849B2 (ja) |
EP (1) | EP2505863B1 (ja) |
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Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN103748375A (zh) * | 2011-08-22 | 2014-04-23 | Ntn株式会社 | 等速万向接头及其制造方法 |
WO2015076051A1 (ja) * | 2013-11-22 | 2015-05-28 | Ntn株式会社 | 固定式等速自在継手 |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
KR101336506B1 (ko) * | 2011-11-16 | 2013-12-03 | 현대위아 주식회사 | 차량용 볼타입 등속조인트 |
JP6165497B2 (ja) | 2012-08-03 | 2017-07-19 | Ntn株式会社 | 等速自在継手用保持器およびこれを組み込んだ固定式等速自在継手、並びにこの固定式等速自在継手を組み込んだドライブシャフト |
CN114294340B (zh) * | 2021-12-30 | 2023-06-20 | 湖南三一中型起重机械有限公司 | 一种自适应联轴机构及工程机械 |
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- 2010-11-25 CN CN201080053480.8A patent/CN102667202B/zh not_active Expired - Fee Related
- 2010-11-25 EP EP10833246.1A patent/EP2505863B1/en not_active Not-in-force
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Also Published As
Publication number | Publication date |
---|---|
US8684849B2 (en) | 2014-04-01 |
CN102667202A (zh) | 2012-09-12 |
JP2011133107A (ja) | 2011-07-07 |
US20120220382A1 (en) | 2012-08-30 |
EP2505863A4 (en) | 2013-06-05 |
EP2505863A1 (en) | 2012-10-03 |
EP2505863B1 (en) | 2019-09-11 |
CN102667202B (zh) | 2015-07-22 |
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