JP2008025650A - Constant velocity joint - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To control the generation of induced thrust force and to reduce processing costs and material costs. <P>SOLUTION: When axes X1, X2 of a first shaft 12 and a second shaft 18 are matched to each other and coaxial, first to third imaginary lines T1 to T3, connecting centers O1, O4 (center O2 and center O5, center O3 and center O6) of a set of balls 28a, 28d (ball 28b and ball 28e, ball 28c and ball 28f) spaced by 180 degrees in the circumferential direction and arranged respectively facing each other with an inner ring 34 therebetween, are respectively set to be inclined at a specified angle against a plane S perpendicular to the axes X1, X2 of the first shaft 12 and second shaft 18, and the centers O1 to O6 of the balls 28a to 28f are all arranged to be positioned on the same plane. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a bar field type constant velocity joint that connects one transmission shaft and the other transmission shaft in a driving force transmission portion of an automobile, for example.

  Conventionally, in a driving force transmission unit of an automobile, a constant velocity joint that connects one transmission shaft and the other transmission shaft and transmits rotational driving force to each axle is used.

  A triport type constant velocity joint according to this type of prior art includes a triport member in which three leg shafts are spaced apart at an angle of 120 degrees along the circumferential direction and protruded radially outward. It is basically composed of a cylindrical outer ring that rotates integrally with the three leg shafts engaged with the track grooves, and transmits rotational torque at a constant speed regardless of the operating angle of the two shafts. It is provided so that the relative displacement of can be permitted. In this case, in order to reduce the frictional resistance between the leg shaft and the track groove, a spherical roller is rotatably attached to the leg shaft.

  In the triport type constant velocity joint according to the prior art, when the rotational torque is transmitted with the operating angle formed by the two axes, the spherical roller of each leg shaft reciprocates in the axial direction of the outer ring within the track groove. Rotational torque is transmitted. As for the period of this reciprocating motion, one reciprocating motion is performed per one rotation (360 degrees) of the outer ring and the tripart member. During this reciprocating motion, the intersecting angle between the axis of the spherical roller and the axis of the outer ring changes continuously, and the spherical roller comes into contact with the track groove in an oblique state. The rolling motion is not performed smoothly, and the reciprocating motion is carried out with sliding, so that the frictional force at each contact portion increases.

  In other words, since the three leg shafts of the tripod member repeat the same reciprocating motion every 120 degrees of rotation, a periodic induced thrust force is generated in the axial direction of the outer ring and the tripart member, and this induced thrust force is generated by the engine. It resonates with the mounting means of the transmission or differential device, and is one of the causes of vehicle vibration.

  Therefore, in order to reduce the induced thrust force, for example, in Patent Document 1, each leg shaft is inclined to a plane perpendicular to the axis of the tripod member and a first inclination angle (α), respectively. There is disclosed a constant velocity joint in which outer ring guide grooves are provided in a predetermined angle direction with each leg shaft, and the central axis of the guide groove is inclined at a second inclination angle (β) with the axial direction of the tripod member. Yes.

  Further, Patent Document 2 includes a joint member having three arms (leg shafts) that rotatably support the roller, and each of the three arms is connected to the joint member and the rotation axis of the shaft element. A constant velocity joint inclined at a predetermined angle with respect to a vertical plane is disclosed.

  Further, Patent Document 3 is provided with three trunnion journals (leg shafts) having an axis AT distributed 120 degrees along the circumferential direction of the axis of the transmission shaft, and the axis of each trunnion journal is the transmission shaft. There is disclosed a constant velocity joint that is inclined at a predetermined angle without being orthogonal to the axis.

  Furthermore, in Patent Document 4, each of the three leg shafts of the tripart member is inclined by an inclination angle (α) on a plane including the axis with respect to a line perpendicular to the axis of the tripod member. A constant velocity joint is disclosed.

  Furthermore, Patent Document 5 discloses a constant velocity joint in which the axis of each leg shaft is inclined at a predetermined angle with respect to a vertical plane crossing the axis of the tripod member.

JP-A-7-103250 Japanese National Patent Publication No. 11-508673 JP-A-7-91457 JP-A-61-266830 Japanese Utility Model Publication No. 63-115927

  However, in the constant velocity joints disclosed in Patent Documents 1 to 5, it is necessary to form each leg shaft of the triport member so as to be inclined at the same inclination angle with respect to a plane perpendicular to the axis of the triport member. There is a problem that the processing cost and the material cost are increased as compared with the tripport member conventionally used.

  Patent Documents 1 to 5 all relate to sliding type triport type constant velocity joints, and the prior art for reducing induced thrust with respect to fixed type barfield type constant velocity joints provided on the tire side is as follows. There is nothing.

  The present invention has been made in view of the above points, and provides a barfield type constant velocity joint capable of suppressing generation of induced thrust force and reducing processing cost and material cost. Objective.

In order to achieve the above object, the present invention provides an outer member connected to one of two intersecting shafts, having a plurality of first guide grooves having an inner diameter surface and extending in the axial direction, and having one end portion opened. Members,
An inner ring connected to the other of the two shafts, extending in the axial direction and having the same number of second guide grooves as the first guide grooves;
A plurality of balls that are arranged to roll between the first guide groove and the second guide groove and transmit torque;
A retainer having a holding window for storing the balls;
With
When the axes of the two axes coincide with each other and are coaxial, they are first to third imaginary that are 180 degrees apart along the circumferential direction and connect the centers of a pair of balls that are opposed to each other with the inner ring in between. Each of the lines is set to be inclined at a predetermined angle with respect to a plane orthogonal to the biaxial axes, and the centers of the plurality of balls are all set on the same plane. Features.

  In this case, when at least one inclination angle is set to be different from the other two inclination angles in relation to the inclination angles of the first to third imaginary lines with respect to the plane orthogonal to the two axes. Good.

  For example, the inclination angle (β) of the second imaginary line with respect to a plane orthogonal to the biaxial axis is different from the inclination angle (α) of the first imaginary line and the inclination angle (γ) of the third imaginary line. And the inclination angle (α) of the first imaginary line and the inclination angle (γ) of the third imaginary line are respectively set equal (α ≠ β, β ≠ γ, α = γ), or The inclination angles (α, β, γ) of the first to third imaginary lines with respect to the plane orthogonal to the two axes may be set to be different (α ≠ β, β ≠ γ, α ≠ γ).

  According to the present invention, when the axes of the two axes coincide with each other and are coaxial, the first is formed by connecting the centers of a pair of balls that are spaced apart by 180 degrees along the circumferential direction and are opposed to each other with an inner ring in between. The third imaginary line is set so as to be inclined at a predetermined angle with respect to the plane orthogonal to the biaxial axis, and the centers of the plurality of balls are all set on the same plane. As a result, the motions of the balls having a driving force transmission function between the two axes are not all the same, and the reciprocating motion is irregular. Therefore, the induced thrust force of the rotational tertiary component is reduced and the generation of vibrations is reduced. It is suppressed.

  In other words, in the prior art, the centers of a plurality of balls are positioned so that they are all included in a plane perpendicular to the biaxial axis, and when the rotational driving force is transmitted between the two axes, each ball performs the same reciprocating motion. In the present invention, the reciprocating motion of at least one set of balls is set to be different from the reciprocating motions of the other balls. As a result, the operational balance is lost, and the induced thrust force of the rotational tertiary component can be reduced.

  Further, in the present invention, the axial line of the hole portion on which the shaft member is axially attached to the inner ring that has been conventionally used is inclined at a predetermined angle without being orthogonal to the inner ring. Since it can be manufactured easily, processing costs and material costs can be reduced.

  According to the present invention, the following effects can be obtained.

  That is, the motions of the balls having the driving force transmission function between the two axes are not all the same, and the reciprocating motion is irregular, so that it is possible to reduce the induced thrust force of the rotational tertiary component. Moreover, it can manufacture simply by making the hole part formed in the center part of an inner ring incline with respect to the axis line of this inner ring. As a result, processing costs and material costs can be reduced.

  Preferred embodiments of the constant velocity joint according to the present invention will be described below and described in detail with reference to the accompanying drawings.

  In FIG. 1, reference numeral 10 indicates a constant velocity joint according to an embodiment of the present invention. In the following description, the vertical cross section refers to a cross section along the axial direction of the first shaft 12 and the second shaft 18, and the horizontal cross section refers to a cross section orthogonal to the axial direction.

  The constant velocity joint 10 is fixedly connected to one end portion of the first shaft 12 and is integrally connected to one end portion of the first shaft 12 and has a bottomed cylindrical outer cup (outer member) 16 having an opening 14 and one end portion of the second shaft 18. The inner member 22 is basically composed of a hole portion of the outer cup 16.

  As shown in FIGS. 1 and 4, the inner wall of the outer cup 16 has a spherical inner surface 24, and the inner surface 24 extends along the axial direction and around the axis. Six first guide grooves 26a to 26f are formed at intervals of 60 degrees. In this case, each of the first guide grooves 26a (26b to 26f) has a curved longitudinal section, and each transverse section is formed in a single arc shape.

  The inner member 22 is formed on the inner ring 34 in which a plurality of second guide grooves 32 a to 32 f corresponding to the first guide grooves 26 a to 26 f are formed along the circumferential direction of the outer peripheral surface, and the inner wall surface of the outer cup 16. The first guide grooves 26a to 26f formed and the second guide grooves 32a to 32f formed on the outer diameter surface of the inner ring 34 are arranged so as to be able to roll, and a plurality of (this book In the embodiment, six balls) 28a to 28f and a plurality of holding windows 36 for holding the balls 28a to 28f are formed along the circumferential direction, and are interposed between the outer cup 16 and the inner ring 34. And a retainer 38.

  The inner ring 34 is spline-fitted to one end of the second shaft 18 through a hole 39 formed so as to penetrate along the axial direction of the second shaft 18, or the annular groove of the second shaft 18. It is integrally fixed to the end of the second shaft 18 via a ring-shaped locking member 40 attached to the head. A plurality of second guide grooves 32 a to 32 f are formed on the outer diameter surface of the inner ring 34 so as to correspond to the first guide grooves 26 a to 26 f of the outer cup 16 and are spaced apart at equal angles along the circumferential direction. .

  The balls 28a to 28f are formed by, for example, steel balls having the same shape, and extend in the circumferential direction between the first guide grooves 26a to 26f of the outer cup 16 and the second guide grooves 32a to 32f of the inner ring 34. Are arranged so as to be able to roll one by one at an equal angle.

  The balls 28a to 28f transmit the rotational torque of the second shaft 18 to the first shaft 12 through the inner ring 34 and the outer cup 16, and the first guide grooves 26a to 26f and the second guide grooves 32a to 32f. By rolling along the configured guide track, the relative displacement in the intersecting angular direction between the second shaft 18 (inner ring 34) and the first shaft 12 (outer cup 16) is enabled. is there. At that time, the rotational torque is suitably transmitted from any direction between the first shaft 12 and the second shaft 18.

  The outer cup 16 has an opening portion 14 formed on one end side and a back portion 46 formed by a closed end on the other end side.

  The constant velocity joint 10 according to the present embodiment is basically configured as described above. Next, the operation, action, and effect will be described.

  When the second shaft 18 rotates, the rotational torque is transmitted from the inner ring 34 to the outer cup 16 via the balls 28a to 28f, and the first shaft 12 maintains a constant velocity with the second shaft 18 in a predetermined direction. Rotate to.

  At that time, when the crossing angle (operating angle) between the first shaft 12 and the second shaft 18 changes, the ball rolls between the first guide grooves 26a to 26f and the second guide grooves 32a to 32f. The retainer 38 tilts by a predetermined angle under the action of 28a to 28f, and the angular displacement is allowed.

  In this case, the six balls 28a to 28f held by the holding window 36 of the retainer 38 are positioned on the uniform velocity surface or the bisector angle plane between the first shaft 12 and the second shaft 18, thereby driving contact points. Is always maintained on a constant velocity surface to ensure constant velocity. As described above, the angular displacement of the first shaft 12 and the second shaft 18 is preferably allowed while maintaining the constant velocity.

  Next, as shown in FIGS. 1 to 3, when the axis X1 of the first shaft 12 and the axis X2 of the second shaft 18 coincide with each other and are coaxial (operating angle is zero degrees), 180 along the circumferential direction. Centers O1 and O4 (center O2 and center O5, center O3) of a pair of balls 28a and 28d (ball 28b and ball 28e, ball 28c and ball 28f) that are spaced apart and arranged opposite each other with the inner ring 34 therebetween The first to third imaginary lines T1 to T3 connecting the center O6) and the first axis 12 and the second axis 18 are inclined at a predetermined angle with respect to the plane (S) perpendicular to the axes X1 and X2 of the first axis 12 and the second axis 18, respectively. And the centers O1 to O6 of the plurality (six) balls 28a to 28f are all set on the same plane.

  That is, as shown in FIG. 1, one ball 28a that is vertically spaced apart by 180 degrees along the circumferential direction with respect to the plane (S) perpendicular to the axes X1 and X2 of the first shaft 12 and the second shaft 18. The first imaginary line T1 connecting the center O1 of the second ball 28d and the center O4 of the other ball 28d is inclined by an inclination angle (α), and the axis lines of the first axis 12 and the second axis 18 as shown in FIG. The second imaginary line T2 connecting the center O2 of one ball 28b and the center O5 of the other ball 28e, which are separated by 180 degrees vertically along the circumferential direction, is inclined with respect to the plane (S) orthogonal to X1 and X2. Inclined by an angle (β) and further up and down along the circumferential direction with respect to the plane (S) perpendicular to the axes X1 and X2 of the first shaft 12 and the second shaft 18, as shown in FIG. The center O3 of one ball 28c separated by 180 degrees and the other ball 28f When the third imaginary line T3 connecting the center O6 is inclined by the inclination angle (γ), at least one of the inclination angles (α, β, γ) of the three pairs of balls 28a to 28f is It is set so as to be different from other inclination angles, and the centers O1 to O6 of the six balls 28a to 28f are all included in the same plane.

  In the present embodiment, as shown in FIGS. 1 to 3, the inclination angle (β) by the second imaginary line T2 is the inclination angle (α) by the first imaginary line T1 and the inclination angle by the third imaginary line T3 ( and the inclination angle (α) by the first virtual line T1 and the inclination angle (γ) by the third virtual line T3 are respectively set equal (α ≠ β, β ≠ γ, α = γ), and the centers O1 to O6 of the six balls 28a to 28f are all included on the same plane.

  Alternatively, the inclination angles (α, β, γ) by the first to third virtual lines T1 to T3 are set to be different (α ≠ β, β ≠ γ, α ≠ γ), and the six The centers O1 to O6 of the balls 28a to 28f may be set so as to be included on the same plane.

  The inclination angles (α, β, γ) of the balls 28a to 28f by the first to third imaginary lines T1 to T3 are inclined to the opening 14 side of the outer cup 16 or inclined to the back portion 46 side. Any of cases may be sufficient.

  Therefore, when a predetermined operating angle is set by the first shaft 12 and the second shaft 18, the operation of the balls 28a to 28f corresponding to the rotation angle of the constant velocity joint 10 according to the present embodiment, and a comparative example The operation of the balls 28a to 28f corresponding to the rotation angle of the constant velocity joint 100 will be compared in detail below. Note that the same components as those of the constant velocity joint 10 according to the present embodiment are denoted by the same reference numerals, and detailed description thereof is omitted.

  In the constant velocity joint 100 according to this comparative example, as shown in FIG. 6, the center O1 (O2, O3) and the other ball 28d of one ball 28a (28b, 28c) spaced apart by 180 degrees along the circumferential direction. The first to third imaginary lines T1 to T3 connecting the centers O4 (O5 and O6) of (28e, 28f) are set to be orthogonal to the axis lines X1 and X2 of the first axis 12 and the second axis 18, respectively. In addition, the centers O1 to O6 of the six balls 28a to 28f are all set on the plane (S) perpendicular to the axis lines X1 and X2 of the first shaft 12 and the second shaft 18. Thus, it is different from the constant velocity joint 10 according to the present embodiment.

  In the comparative example, the six balls 28a to 28f are arranged so as to be spaced apart by 60 degrees in the circumferential direction along the second guide grooves 32a to 32f of the inner ring 34. The form is the same.

  In addition, the rotation angle is the initial state when the center O1 of the ball 28a is positioned upward and coincides with the vertical line, with the rotation angle being 0 degree, and hereinafter, the state rotated once every 60 degrees along the arrow direction. (0 degree → 60 degree → 120 degree → 180 degree → 240 degree → 300 degree → 0 degree).

(1) FIGS. 7A to 7F show a state in which the constant velocity joint 100 according to the comparative example is rotated once every 60 degrees from the initial state.

  In this case, as shown in FIGS. 7A and 7D, when the rotation angle is 0 degree and the rotation angle is 180 degrees, the center O1 of the one ball 28a and the center of the other ball 28d that are separated by 180 degrees along the circumferential direction. A first imaginary line T1 connecting O4 is perpendicular to the first axis 12 and the second axis 18 when the vertical plane S (coaxial) between the first axis 12 and the second axis 18 is 0 degree (coaxial). It is in a state of being inclined by the same inclination angle (A) in opposite directions to each other. That is, when the rotation angle is 0 degree, the first imaginary line T1 (line connecting the center O1 of the ball 28a and the center O4 of the ball 28d) with respect to the vertical plane is inclined by a predetermined angle (A) toward the opening 14 side of the outer cup 16. On the other hand, at a rotation angle of 180 degrees, the first imaginary line T1 with respect to the vertical plane is inclined by the same angle (A) toward the inner portion 46 of the outer cup 16 in the opposite direction.

  Further, as shown in FIGS. 7C and 7F, in the state of the rotation angle of 120 degrees and the rotation angle of 300 degrees, the center O2 of one ball 28b and the center O5 of the other ball 28e that are separated by 180 degrees along the circumferential direction. Is perpendicular to the first axis 12 and the second axis 18 when the operating angle formed by the first axis 12 and the second axis 18 is 0 degree (coaxial). The same inclination angle (A) in opposite directions to each other. That is, at the rotation angle of 120 degrees, the second imaginary line T2 with respect to the vertical plane S is inclined by a predetermined angle (A) toward the opening 14 side of the outer cup 16, while at the rotation angle of 300 degrees, the outer cup 16 is opposite to the above. Is inclined at the same angle (A) toward the back 46 side.

  Further, as shown in FIGS. 7B and 7E, in the state of the rotation angle of 60 degrees and the rotation angle of 240 degrees, the center O3 of one ball 28c and the center O6 of the other ball 28f that are separated by 180 degrees along the circumferential direction. Is perpendicular to the first axis 12 and the second axis 18 when the operating angle formed by the first axis 12 and the second axis 18 is 0 degree (coaxial). The same inclination angle (A) in opposite directions to each other. That is, at the rotation angle of 60 degrees, the third virtual line T3 with respect to the vertical surface S is inclined by a predetermined angle (A) toward the opening 14 side of the outer cup 16, while at the rotation angle of 240 degrees, the third virtual line T3 with respect to the vertical surface S is inclined. Contrary to the above, the line T3 is inclined by the same angle (A) toward the back 46 side of the outer cup 16.

  Thus, the first to third imaginary lines T1 to T3 that respectively connect the centers O1 to O6 of the pair of balls 28a to 28f that are spaced 180 degrees along the circumferential direction and are opposed to each other, It is set to be orthogonal to the axis lines X1 and X2 of the first axis 12 and the second axis 18, and is set to be positioned on a plane orthogonal to the axis lines X1 and X2 of the first axis 12 and the second axis 18. In the constant velocity joint 100 according to the comparative example, the first to third imaginary lines T1 to T3 operate so as to be inclined by the same inclination angle (A) on the opening 14 side and the back part 46 side, respectively. Corresponding to the rotation angle, the six balls 28a to 28f corresponding to the first to third imaginary lines T1 to T3 perform the same reciprocating motion along the guide track.

(2) FIGS. 5A to 5F show a state in which the constant velocity joint 10 according to the present embodiment is rotated once every 60 degrees from the initial state.

  In this case, as shown in FIGS. 5A and 5D, when the rotation angle is 0 degree and the rotation angle is 180 degrees, the centers O1 and O4 of the pair of balls 28a and 28d that are separated by 180 degrees along the circumferential direction are connected. The first imaginary line T1 is a vertical plane S (a plane perpendicular to the first axis 12 and the second axis 18 when the operating angle between the first axis and the second axis 14 is 0 degree (coaxial)). In contrast, they are inclined at different angles in opposite directions. That is, at the rotation angle of 0 degree, the first imaginary line T1 is inclined by the inclination angle (B) toward the opening 14 side of the outer cup 16 with respect to the vertical plane S. Thus, the first imaginary line T1 is slightly inclined toward the inner portion 46 side of the outer cup 16 by an inclination angle (E). In this case, the inclination angle is B> E.

  Further, as shown in FIGS. 5C and 5F, in the state of the rotation angle of 120 degrees and the rotation angle of 300 degrees, the centers O3 and O6 of a pair of balls 28c and 28f that are separated by 180 degrees along the circumferential direction are connected. The third virtual line T3 is a vertical plane S (a plane orthogonal to the first axis 12 and the second axis 18 when the operating angle between the first axis 12 and the second axis 18 is 0 degree (coaxial)). In contrast, the first virtual line T1 is inclined at an angle different from the inclination angle (B, E). That is, at the rotation angle of 120 degrees, the third imaginary line T3 with respect to the vertical plane S is inclined toward the opening 14 side of the outer cup 16 by an inclination angle (D) smaller than the inclination angle (B) of the first imaginary line T1. On the other hand, when the rotation angle is 300 degrees, the third imaginary line T3 with respect to the vertical plane S is opposite to the above and the inclination angle is greater than the inclination angle (E) of the first imaginary line T1 on the back 46 side of the outer cup 16. Inclined by (C).

  Further, as shown in FIGS. 5B and 5E, in the state of the rotation angle of 60 degrees and the rotation angle of 240 degrees, the centers O2 and O5 of the pair of balls 28b and 28e that are separated by 180 degrees along the circumferential direction are connected. The second virtual line T2 is a vertical plane S (a plane perpendicular to the first axis 12 and the second axis 18 when the operating angle between the first axis 12 and the second axis 18 is 0 degree (coaxial)). On the other hand, the tilt angle is different from the tilt angle (B, E) of the first virtual line T1 and tilted at the same angle as the tilt angle (C, D) of the third virtual line T3. That is, at the rotation angle of 60 degrees, the second imaginary line T2 with respect to the vertical plane is slightly inclined toward the opening 14 side of the outer cup 16 by an inclination angle (C) smaller than the inclination angle (B) of the first imaginary line T1. On the other hand, at the rotation angle of 240 degrees, the second imaginary line T2 with respect to the vertical plane S is only inclined angle (D) larger than the inclination angle (E) of the first imaginary line T1 on the back 46 side of the outer cup 16. Inclined.

  In this way, only the first virtual line T1 is inclined at a different inclination angle from the other second virtual lines T2 and the third virtual line T3, and the second virtual line T2 and the third virtual line T3 are inclined at the same angle. In the constant velocity joint 10 according to the present embodiment in which the centers O1 to O6 of the balls 28a to 28f are set on the same plane, the first virtual line T1 is the other second virtual line T2. And the third imaginary line T3 is operated so as to be inclined at different inclination angles on the opening 14 side and the back part 46 side, respectively, and is connected by the first imaginary line T1 corresponding to the rotation angle. Only one set of balls 28a, 28d reciprocates differently from the other balls 28b, 28c, 28e, 28f connected by the other second and third virtual lines T2, T3. In the present embodiment, it is determined that the balls 28b, 28e, 28c, and 28f connected by the second and third virtual lines T2 and T3 are performing the same operation.

  Next, FIGS. 8 to 9 show simulation results of the order of rotation and the induced thrust force between the constant velocity joint 100 according to the comparative example and the constant velocity joint 10 according to the present embodiment. In this case, the simulation was performed with the operating angle (joint angle) formed by the first shaft 12 and the second shaft 18 set to 8 degrees.

  As shown in FIG. 8 and FIG. 9, when the induced thrust force of the rotational tertiary component in the comparative example is compared with the induced thrust force of the rotational tertiary component in the present embodiment, in the present embodiment, the rotational tertiary component is compared. Since the peaks in the component are low, it can be understood that the induced thrust force of the rotational tertiary component is reduced compared to the comparative example.

  As described above, in the present embodiment, a pair of balls 28a and 28d (ball 28b and ball 28e, ball 28c and ball 28b and balls 28a and 28d, which are spaced apart from each other by 180 degrees along the circumferential direction and are disposed opposite to each other with the inner ring 34 therebetween. 28f), the first to third imaginary lines T1 to T3 connecting the centers O1 and O4 (center O2 and center O5, center O3 and center O6), respectively, are axis lines X1 and X1 of the first axis 12 and the second axis 18, respectively. By setting so as to be inclined at a predetermined angle with respect to the plane (S) orthogonal to X2, and by setting so that the centers O1 to O6 of the six balls 28a to 28f are all located on the same plane, Since the motions of the balls 28a to 28f are not all the same and are irregular reciprocating motions, it is possible to reduce the induced thrust force of the rotational tertiary component and suppress the occurrence of vibration.

  In other words, in the constant velocity joint 100 according to the comparative example, the plurality of balls 28a to 28f perform the same reciprocating motion along the guide track between the first guide grooves 26a to 26f and the second guide grooves 32a to 32f, respectively. In this embodiment, the operation of at least one set of balls 28a and 28d is the operation of the other two sets of balls 28b, 28e, 28c, and 28f. By setting differently, the operation balance of the six balls 28a to 28f is lost, and the induced thrust force of the rotational tertiary component can be reduced.

  Furthermore, in the constant velocity joint 10 according to the present embodiment, as shown in FIG. 10, a ball 28 a is formed using an inner ring 34 in which six second guide grooves 32 a to 32 f that have been conventionally used are formed. The inner ring 34 as a whole is inclined at a predetermined angle (N) with respect to the vertical plane (S) while the recess of the second guide groove 32a to be stored is positioned above. By tilting and forming the hole 39 through which the second shaft 18 is penetrated, only the inclination angle (α) of the first imaginary line T1 is changed to the inclination angles of the other second and third imaginary lines T2, T3 ( (.beta., .gamma.) can be manufactured differently (.alpha..noteq..beta., .alpha..noteq..gamma., .beta. =. gamma.).

  As described above, in the constant velocity joint 10 according to the present embodiment, the axis of the hole 39 on which the second shaft 18 is axially attached to the inner ring 34 that has been used conventionally is set to the inner ring 34. By forming in a state where it is inclined at a predetermined angle without being orthogonal to each other, it can be easily manufactured, so that processing costs and material costs can be reduced. That is, in the present embodiment, the second guide grooves 32a to 32f formed in the inner ring 34 are not inclined, but the hole 39 formed at the center of the inner ring 34 is not inclined. It can be simply manufactured by perforating with the axis inclined.

It is a longitudinal cross-sectional view along the axial direction of the constant velocity joint which concerns on embodiment of this invention. It is a longitudinal cross-sectional view which shows the state which rotated the constant velocity joint shown in FIG. 1 60 degree | times centering on the axis line of a 1st axis | shaft and a 2nd axis | shaft. It is a longitudinal cross-sectional view which shows the state which rotated the constant velocity joint shown in FIG. 2 60 degree | times centering on the axis line of a 1st axis | shaft and a 2nd axis | shaft. FIG. 3 is an arrow view seen from the direction of arrow Z in FIG. 1. 5A to 5F are respectively virtual lines that connect the center of a set of balls to the vertical plane S when the constant velocity joint according to the present embodiment makes one rotation every 60 degrees from the initial state. It is a longitudinal cross-sectional view which shows the inclination state. It is a longitudinal cross-sectional view along the axial direction of the constant velocity joint which concerns on a comparative example. 7A to 7F are imaginary lines connecting the centers of a set of balls to the vertical plane when the constant velocity joint according to the comparative example shown in FIG. 6 makes one rotation every 60 degrees from the initial state. It is a longitudinal cross-sectional view which shows the inclination state. It is a characteristic view which shows the relationship between the rotation order of the constant velocity joint which concerns on a comparative example, and induced thrust force. It is a characteristic view which shows the relationship between the rotation order of the constant velocity joint which concerns on this Embodiment, and an induced thrust force. A state in which the hole in which the second shaft is axially mounted is drilled obliquely using the conventionally used inner ring, and the second axis is axially attached to the hole formed in the inner ring. It is a side view.

Explanation of symbols

DESCRIPTION OF SYMBOLS 10 ... Constant velocity joint 12 ... 1st axis | shaft 14 ... Opening part 16 ... Outer cup 18 ... 2nd axis | shaft 24 ... Inner diameter surface 26a-26f ... 1st guide groove 32a-32f ... 2nd guide groove 34 ... Inner ring 36 ... Holding window 38 ... Retainer 39 ... Hole 46 ... Back part T1-T3 ... Virtual line S ... Vertical plane (alpha), (beta), (gamma) ... Inclination angle O1-O6 ... Center

Claims (4)

An outer member connected to one of two intersecting shafts, having an inner diameter surface and extending in the axial direction, and having a plurality of first guide grooves open at one end;
An inner ring connected to the other of the two shafts, extending in the axial direction and having the same number of second guide grooves as the first guide grooves;
A plurality of balls that are arranged to roll between the first guide groove and the second guide groove and transmit torque;
A retainer having a holding window for storing the balls;
With
When the axes of the two axes coincide with each other and are coaxial, they are first to third imaginary that are 180 degrees apart along the circumferential direction and connect the centers of a pair of balls that are opposed to each other with the inner ring in between. Each of the lines is set to be inclined at a predetermined angle with respect to a plane orthogonal to the biaxial axes, and the centers of the plurality of balls are all set on the same plane. Characteristic constant velocity joint. The constant velocity joint according to claim 1,
In relation to the inclination angle of the first to third imaginary lines with respect to the plane orthogonal to the two axes, at least one inclination angle is set to be different from the other two inclination angles, respectively. Constant velocity joint. In the constant velocity joint according to claim 2,
An inclination angle (β) of the second imaginary line with respect to a plane orthogonal to the biaxial axis is different from an inclination angle (α) of the first imaginary line and an inclination angle (γ) of the third imaginary line. And the inclination angle (α) of the first imaginary line and the inclination angle (γ) of the third imaginary line are set to be equal (α ≠ β, β ≠ γ, α = γ), respectively. Constant velocity joint. In the constant velocity joint according to claim 2,
The inclination angles (α, β, γ) of the first to third imaginary lines with respect to the plane orthogonal to the two axes are set to be different (α ≠ β, β ≠ γ, α ≠ γ). A constant velocity joint.

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