JP2013061018A - Constant velocity joint - Google Patents

Abstract

A constant velocity joint capable of reliably preventing a shaft from coming off from an insertion hole of an inner member is provided.
A second snap ring engaging portion, a second snap ring engaging portion, and a second snap ring engaging portion are formed on a tip end side of a shaft among two side surfaces of the second snap ring concave portion facing each other in the axial direction. The first snap ring engaging portion 36a of the opposing first snap ring recess 36 is formed to be inclined. Thereby, only a part of the snap ring 70 is pressed by the second snap ring engaging portion 63a, and only a part of the snap ring 70 is applied with a load in the diameter reducing direction. For this reason, the snap ring 70 is not reduced in diameter at all, and the shaft 60 can be reliably prevented from coming off from the insertion hole 34 of the inner member 30.
[Selection] Figure 3

Description

  The present invention relates to a constant velocity joint used for a driving force transmission unit or the like of a vehicle.

  As an example of a conventional constant velocity joint, a ball type constant velocity joint described in Japanese Patent Application Laid-Open No. 2006-266460 (Patent Document 1) is known. This ball type constant velocity joint is formed in a bottomed cylindrical shape, and has an outer ring in which a plurality of outer ring ball grooves are formed on the inner peripheral surface, and a plurality of inner ring ball grooves formed on the outer peripheral surface. The tip is inserted into the formed inner member, a plurality of balls that are disposed between the outer ring ball groove and the inner member ball groove and transmit torque between the outer ring and the inner member, and the insertion hole formed in the inner member. And a shaft connected to the inner member.

  The insertion hole of the inner member and the tip of the shaft are spline-fitted, and the first snap ring engagement portion formed at one end of the peripheral wall surface of the insertion hole and the second snap ring formed at the tip of the shaft A C-shaped snap ring is engaged with the engaging portion, and the shaft is connected to the inner member so as not to be relatively rotatable. The first snap ring engaging portion has a tapered shape that gradually decreases in diameter toward the back side due to processing factors.

  In such a ball type constant velocity joint, the inner member can swing relative to the outer ring by rolling the ball between the outer ring ball groove and the inner member ball groove. Such a ball type constant velocity joint is different from the sliding tripod type constant velocity joint in that the inner member cannot slide in the axial direction with respect to the outer ring, but the swing angle of the inner member with respect to the outer ring is large. Therefore, it is preferably used as an outboard joint of a drive shaft installed on the front side of the vehicle.

JP 2006-266460 A (pages 3 to 5, FIG. 1)

  As described above, in the ball type constant velocity joint, the inner member cannot slide in the axial direction with respect to the outer ring, so that when the load in the direction of being pulled out from the inner member is applied to the shaft, the snap ring is Pressed by the second snap ring engaging portion formed on the shaft, the outer periphery side of the snap ring is pressed by the tapered first snap ring engaging portion over the entire circumference, the snap ring is reduced in diameter, and the shaft is inside There was a risk of being pulled out of the member.

  The present invention has been made in view of such circumstances, and an object of the present invention is to provide a constant velocity joint that can reliably prevent the shaft from coming off from the insertion hole of the inner member.

  (Claim 1) A constant velocity joint according to the present invention is provided with an outer ring formed in a bottomed cylindrical shape, and is arranged on the inner side of the outer ring so as to be able to swing relative to the outer ring, thereby forming an insertion hole. A plurality of torque transmission members disposed between the outer ring and the inner member, engaged with the outer ring and the inner member, and configured to transmit torque between the outer ring and the inner member; A fitting portion is formed on the outer peripheral surface of the side, a shaft that is inserted into the insertion hole and connected to the inner member, and an axial engagement with the insertion hole and the fitting portion. And a C-shaped snap ring for preventing the shaft from coming off from the inner member, and a plurality of inner circumferential surfaces of the insertion holes of the inner member along the axial direction of the inner member. A female spline is formed and crosses the female spline A first snap ring engaging portion is formed, and a plurality of male splines are formed on the outer peripheral surface of the fitting portion of the shaft along the axial center direction of the shaft so as to cross the male spline. A second snap ring engaging portion is formed, and the male spline is fitted to the female spline, and the snap ring is disposed between the first snap ring engaging portion and the second snap ring engaging portion facing each other. Engaged, the shaft is connected to the inner member in a relatively non-rotatable manner, and the first snap ring engaging portion and the second snap ring engaging portion are inclined with respect to each other.

  (Claim 1) According to the present invention, the first snap ring engaging portion and the second snap ring engaging portion are inclined to each other. Thereby, when the load to the direction pulled out from an inner member acts on a shaft, only a part of 2nd snap ring engaging part presses a snap ring. That is, only a part of the snap ring in the circumferential direction is pressed by the second snap ring engaging part, and the other part of the snap ring is not pressed by the second snap ring engaging part. For this reason, a load in the reduced diameter direction is applied only to a part of the snap ring in the circumferential direction. Even if a load in the reduced diameter direction is applied to a part of the snap ring in the circumferential direction, no load in the reduced diameter direction is applied to the other part at all. The snap ring is not reduced in diameter only by moving in the direction in which the load is applied along the ring engaging portion. Further, even if a load in the reduced diameter direction is applied to a part of the snap ring in the circumferential direction, the male spline at the intersection of the open end of the snap ring with the inclined second snap ring engaging portion The snap ring is prevented from being reduced in diameter. As described above, since the snap ring is reliably prevented from being reduced in diameter, it is possible to reliably prevent the shaft from coming off from the insertion hole of the inner member.

It is sectional drawing which showed one Embodiment of the constant velocity joint by this invention. It is a top view of a snap ring. FIG. 2 is an enlarged detailed cross-sectional view of FIG. 1 showing a shaft, an inner member, and a snap ring. It is sectional drawing showing the shaft, the inner member, and snap ring of the conventional constant velocity joint as a comparative example. (A) ... It is the Y section enlarged view of FIG. (B) is an enlarged view of a Z part in (A). (C) ... It is a figure showing the diameter reduction state of the snap ring in the conventional constant velocity joint. (A) ... It is the X section enlarged view of FIG. (B) ... It is a W section enlarged sectional view of (A). (C) is a view showing the state of the snap ring in the constant velocity joint of the present invention. It is a figure showing the shaft of the other embodiment of the constant velocity joint by this invention, the inner member, and the snap ring.

(Constant velocity joint structure of the present invention)
Hereinafter, an embodiment in which the constant velocity joint of the present invention is embodied will be described with reference to the drawings. First, the whole structure of the constant velocity joint 10 of this embodiment is demonstrated using FIG. As shown in FIG. 1, the constant velocity joint 10 is a ball-type constant velocity joint. The constant velocity joint 10 includes an outer ring 20, an inner member 30, a plurality of balls 40 (torque transmission member), a cage 50, a shaft 60, and a snap ring 70.

  The outer ring 20 is formed in a cup shape (bottomed cylindrical shape) having an opening on the right side of FIG. On the outer side of the cup bottom of the outer ring 20 (left side in FIG. 1), a connecting shaft 21 is integrally formed so as to extend in the direction of the outer ring axis. Here, the outer ring axial direction means a direction passing through the central axis of the outer ring 20, that is, a rotation axis direction of the outer ring 20. The connecting shaft 21 is connected to another power transmission shaft. The inner peripheral surface 22 of the outer ring is formed in a concave spherical surface. On the inner peripheral surface 22 of the outer ring 20, a plurality of outer ring ball grooves 23 having a substantially arc-shaped cross section in the direction orthogonal to the outer ring axis are formed in an arc shape extending substantially in the direction of the outer ring axis. These plural (six in this embodiment) outer ring ball grooves 23 are formed at equal intervals in the circumferential direction (60 ° intervals in this embodiment) when viewed in a cross section cut in the radial direction.

  The inner member 30 is formed in an annular shape and is disposed inside the outer ring 20. The outer peripheral surface 31 of the inner member 30 is formed in a convex spherical shape. A plurality of inner member ball grooves 32 whose inner member axis orthogonal cross section is substantially arc-shaped concave are formed in an arc shape on the outer peripheral surface 31 of the inner member 30 so as to extend substantially in the inner member axial direction. Here, the inner member axial direction means a direction passing through the central axis of the inner member 30, that is, a rotation direction of the inner member. A plurality (six in this embodiment) of inner member ball grooves 32 are formed in the outer ring 20 at regular intervals in the circumferential direction (60 ° intervals in this embodiment) when viewed in a cross section cut in the radial direction. The same number of outer ring ball grooves 23 are formed. That is, each inner member ball groove 32 is positioned to face each outer ring ball groove 23 of the outer ring 20.

  Between the adjacent inner member ball grooves 32, protrusions 33 that protrude radially outward are formed. An insertion hole 34 is formed through the axial center (center) of the inner member 30 in the inner member axial direction. A plurality of female splines 35 are formed on the inner peripheral surface of the insertion hole 34 along the inner member axial direction.

  A first snap ring recess 36 that makes one turn along the circumferential direction so as to cross the female spline 35 is formed as a recess (removed) at one end of the peripheral wall surface of the insertion hole 34 of the inner member 30. The first snap ring recess 36 opens to one end side in the axial direction of the inner member 30.

  The plurality of balls 40 (torque transmission members) are disposed between the outer ring 20 and the inner member 30 and engage the outer ring 20 and the inner member 30. Specifically, each of the plurality of balls 40 is disposed so as to be sandwiched between the outer ring ball groove 23 of the outer ring 20 and the inner member ball groove 32 of the inner member 30 facing the outer ring ball groove 23. Each ball 40 can roll with respect to each outer ring ball groove 23 and each inner member ball groove 32, and transmits torque between the outer ring 20 and the inner member 30. With such a structure, the inner member 30 can swing relative to the outer ring 20.

  The cage 50 is formed in an annular shape and is disposed between the inner peripheral surface 22 of the outer ring 20 and the outer peripheral surface 31 of the inner member 30. The outer peripheral surface 51 of the cage 50 is formed in a partial spherical shape substantially corresponding to the inner peripheral surface 22 of the outer ring, that is, a convex spherical shape. On the other hand, the inner peripheral surface 52 of the cage 50 is formed in a partial spherical shape substantially corresponding to the outer peripheral surface 31 of the inner member 30, that is, a concave spherical shape. The cage 50 is formed with a plurality of substantially rectangular windows 53 penetrating at regular intervals in the circumferential direction (circumferential direction of the cage axis). The same number of the window portions 53 as the balls 40 are formed. In each window portion 53, one ball 40 is accommodated and held.

  A fitting portion 61 is formed at the tip portion of the shaft 60. A plurality of male splines 62 are formed on the outer peripheral surface of the fitting portion 61 along the axial direction of the shaft 60. The male spline 62 of the fitting portion 61 and the female spline 35 of the inner member 30 are spline-fitted, and the fitting portion 61 of the shaft 60 is inserted through the insertion hole 34 of the inner member 30. With such a structure, the inner member 30 and the shaft 60 are connected so as not to rotate relative to each other (to allow torque transmission).

  A groove-like second snap ring recess 63 is formed in the tip of the fitting portion 61 (tip in the axial direction of the shaft 60) so as to traverse the male spline 62 along the circumferential direction.

  A substantially C-shaped snap ring 70 is engaged with the first snap ring recess 36 and the second snap ring recess 63. As shown in FIG. 2, the snap ring 70 has a substantially C shape in which a part of the ring is notched by a notch 70 a when viewed from above. In this embodiment, the cross-sectional shape of the snap ring 70 is a circular shape. This snap ring 70 is engaged in the axial direction (the axial direction of the shaft 60 and the inner member 30) with respect to the first snap ring recess 36 formed in the insertion hole 34 and the second snap ring recess 63 formed in the fitting portion 61. In combination, the shaft 60 is prevented from coming off from the inner member 30.

Next, specific shapes of the first snap ring recess 36 and the second snap ring recess 63 will be described with reference to FIG.
The first snap ring recess 36 is recessed to have a diameter larger than the diameter of the valley of the female spline 35. A tapered first snap ring that gradually decreases in diameter toward the back side (inside the axial direction a of the inner member 30) at the bottom of the first snap ring recess 36 (inside of the inner member 30 in the axial direction a). An engaging portion 36a is formed. The inner member 30 is processed by punching and forming a female spline 35 from one end of the inner member 30 to the other end after the first snap ring recess 36 is formed. The first snap ring engaging portion 36a is formed in a tapered shape in order to prevent formation of burrs and sagging in the first snap ring recess 36 when the female spline 35 is formed. That is, the first snap ring engaging portion 36 a is formed in a taper shape due to processing factors of the inner member 30.

  Of the two side surfaces 63a and 63b facing in the axial direction in the groove-shaped second snap ring recess 63, the side surface on the tip end side of the shaft 60 is a second snap ring engaging portion 63a, The side surface is a central side surface 63b. With the fitting portion 61 inserted through the insertion hole 34, the first snap ring recess 36 and the second snap ring recess 63 are formed at substantially the same position in the direction of the axis A of the shaft 60. Yes.

  In the present invention, the second snap ring engaging portion 63a and the first snap ring engaging portion 36a facing the second snap ring engaging portion 63a are formed to be inclined with respect to each other. In the embodiment shown in FIG. 3, the second snap ring recess 63 is formed to be inclined with respect to a plane B orthogonal to the axis A of the shaft 60. That is, both the second snap ring engaging portion 63 a and the central side surface 63 b of the second snap ring recess 63 are inclined with respect to the surface B orthogonal to the axis A of the shaft 60. On the other hand, the first snap ring engaging portion 36 a of the first snap ring recess 36 is formed in parallel to the surface b orthogonal to the axis a of the inner member 30.

  When the diameter of the snap ring 70 is reduced, the snap ring 70 is completely accommodated in the second snap ring recess 63. That is, the depth of the second snap ring recess 63 is larger than the wire diameter (width) of the snap ring 70. When the snap ring 70 is reduced in diameter, the outer diameter of the snap ring 70 is smaller than the diameter of the peak portion of the female spline 35.

  Next, a method for connecting the inner member 30 and the shaft 60 will be described. First, the snap ring 70 is expanded in diameter, and the snap ring 70 is attached to the second snap ring recess 63 of the shaft 60. Next, in a state where the diameter of the snap ring 70 is reduced, the male spline 62 is fitted to the female spline 35 and the fitting portion 61 is inserted into the insertion hole 34. As described above, when the snap ring 70 is reduced in diameter, the outer diameter of the snap ring 70 is smaller than the diameter of the peak portion of the female spline 35, so that the snap ring 70 has the insertion hole 34 (female spline 35). I can pass.

  When the snap ring 70 completely passes through the insertion hole 34, the snap ring 70 expands in diameter, and a part (substantially half) of the outer peripheral side of the snap ring 70 protrudes into the first snap ring recess 36. In this state, no force is applied to either the diameter increasing direction or the diameter decreasing direction of the snap ring 70, and the snap ring 70 is in a free state. In this state, as described above, a part (substantially half) of the outer peripheral side of the snap ring 70 protrudes (engages) into the first snap ring concave portion 36, and at the inner peripheral side of the snap ring 70. A part (substantially half) protrudes (engages) into the second snap ring recess 63, thereby preventing the shaft 60 from coming off from the inner member 30. In other words, the snap ring 70 engages (abuts) the first snap ring engaging portion 36a and the second snap ring engaging portion 63a facing each other to prevent the shaft 60 from coming off from the inner member 30. Is done. The diameter reduction direction of the snap ring 70 means the center direction (inner side) of the snap ring 70, and the diameter expansion direction of the snap ring 70 means the outer direction of the snap ring 70.

(Description of the operation of a conventional constant velocity joint as a comparative example)
As a comparative example for the constant velocity joint 10 of the present invention, the operation when a load in the direction of being pulled out from the inner member is applied to the shaft in a conventional constant velocity joint will be described with reference to FIGS.
In the conventional constant velocity joint, as shown in FIG. 4, both the first snap ring recess 136 and the second snap ring recess 163 are inclined with respect to the plane B perpendicular to the axis A of the shaft 160. Absent. Therefore, when a load is applied to the shaft 160 in the direction of being pulled out from the inner member 130, the snap ring 170 is pressed by the second snap ring engaging portion 163a over the entire circumference, and the The pressing load P acts in the direction orthogonal to the two snap ring engaging portions 163a ((1) in FIGS. 4 and 5A and 5B).

  Then, the snap ring 170 is pressed by the tapered first snap ring engaging portion 136a over the entire circumference, and the drag is applied to the entire circumference of the snap ring 170 toward the vertical direction of the first snap ring engaging portion 136a. Q acts ((2) in FIG. 5B). Here, the drag force Q is a vertical drag force R acting in a direction orthogonal to the second snap ring engagement portion 163a and a horizontal direction acting in a direction parallel to the second snap ring engagement portion 163a. It is decomposed into drag S. The vertical drag R and the pressing load P are equal. As described above, since the pressing load P acts on the entire circumference of the snap ring 170, the horizontal drag S acts on the entire circumference of the snap ring 170 (FIG. 5C). As a result, the snap ring 170 is reduced in diameter as indicated by the dotted line in FIG. When the diameter of the snap ring 170 is reduced, the snap ring 170 can pass through the insertion hole 134 and the shaft 160 is pulled out from the inner member 130.

(Description of operation of constant velocity joint in this embodiment)
Next, the operation of the constant velocity joint 10 when a load in the direction in which the shaft 60 is pulled out from the inner member 30 is applied to the shaft 60 will be described with reference to FIGS. 3 and 6.
In the constant velocity joint 10 of the present embodiment, the second snap ring engaging portion 63a is inclined with respect to the surface B orthogonal to the axis A of the shaft 60 as described above. For this reason, when a load is applied to the shaft 60 in the direction of detaching from the inner member 30 (the direction of the center A of the shaft 60), the shaft center of the shaft 60 is the most of the second snap ring engaging portions 63a. a Only the portion protruding toward the center side, that is, a part of the second snap ring engaging portion 63 a presses the snap ring 70. That is, only a part of the snap ring 70 in the circumferential direction is pressed by the second snap ring engaging part 63a, and the other part of the snap ring 70 is not pressed by the second snap ring engaging part 63a. Therefore, the pressing load T acts only on a part of the circumferential direction of the snap ring 70 in the direction orthogonal to the second snap ring engaging portion 63a (see FIGS. 3 and 6A and 6B). 1)).

  Then, a part of the snap ring 70 in the circumferential direction is pressed by the first snap ring engaging part 36a, and a drag is applied to a part of the snap ring 70 in the circumferential direction toward the vertical direction of the first snap ring engaging part 36a. U acts ((2) in FIG. 6B). The drag U includes a vertical drag V acting in a direction perpendicular to the second snap ring engagement portion 63a and a horizontal drag W acting in a direction parallel to the second snap ring engagement portion 63a. Is broken down into As described above, since the pressing load T acts only on a part of the snap ring 70, the horizontal drag force W acts only on a part of the snap ring 70 in the circumferential direction (FIG. 6C).

  Even if a horizontal drag force W acts on a part of the snap ring 70 in the circumferential direction, the snap ring 70 other than the portion where the horizontal drag force W is applied has no load in the diameter reducing direction. Since the snap ring 70 is not acting, the snap ring 70 is moved in the direction in which the horizontal drag W acts along the second snap ring recess 63, and the snap ring 70 is not reduced in diameter at all.

  Further, even if a horizontal drag force W acts on a part of the circumferential direction of the snap ring 70, as shown in FIG. 6A, the open end 70b of the snap ring 70 has a second snap ring recess 63. Is caught by the male spline 62 at the intersecting portion (portion connected to the second snap ring engaging portion 63a and the central side surface 63b), and the snap ring 70 is prevented from being reduced in diameter. More specifically, since the second snap ring recess 63 is inclined with respect to the plane B orthogonal to the axis A of the shaft 60, the portion where the male spline 62 and the second snap ring recess 63 intersect is shown in FIG. As shown in A), it is stepped in the direction of the axis A of the shaft 60. For this reason, as described above, the open end 70 b of the snap ring 70 is caught by the male spline 62. As described above, since the diameter reduction of the snap ring 70 is reliably prevented, the shaft 60 can be reliably prevented from coming off from the insertion hole 34 of the inner member 30.

(Other embodiments)
Next, another embodiment of the constant velocity joint 10 according to the present invention will be described with reference to FIG. In this embodiment, as shown in FIG. 7, a first snap ring recess 36 is formed in the middle of the peripheral wall surface of the insertion hole 34 of the inner member 30. The second snap ring recess 63 is also formed in the middle part of the fitting part 61. In the state where the fitting portion 61 is inserted into the insertion hole 34, the formation position of the first snap ring recess 36 and the formation position of the second snap ring recess 63 are substantially the same in the direction of the axis A of the shaft 60. ing. Also in this embodiment, the second snap ring recess 63 is formed to be inclined with respect to the plane B orthogonal to the axis A of the shaft 60. On the other hand, the first snap ring engaging portion 36 a that is the bottom surface of the first snap ring recess 36 is formed in parallel to the surface b orthogonal to the axis a of the inner member 30. That is, the first snap ring engaging portion 36a and the second snap ring engaging portion 63a facing each other are formed to be inclined with respect to each other.

  In this embodiment as well, when a load in the direction of coming out of the inner member 30 is applied to the shaft 60, the second snap ring engaging portion 63a is pushed out to the most proximal side of the shaft center A of the shaft 60. Only the part which is present, that is, a part of the second snap ring engaging portion 63a presses the snap ring 70 ((1) in FIG. 7). And only the part of the circumferential direction of the snap ring 70 is pressed by the 2nd snap ring engaging part 63a, and the other part of the snap ring 70 is not pressed by the 2nd snap ring engaging part 63a. For this reason, as in the above-described embodiment, the pressing load M acts only on a part of the circumferential direction of the snap ring 70 in the direction orthogonal to the second snap ring engaging portion 63a. The horizontal drag N in the direction of diameter reduction acts only on a part of the direction ((2) in FIG. 7). For this reason, similarly to the above-described embodiment, the snap ring 70 can be reliably prevented from coming off from the insertion hole 34 of the inner member 30 without reducing the diameter of the snap ring 70 at all.

  As described above in detail, according to the constant velocity joint 10 of the present invention, as shown in FIGS. 3, 6A, and 7, the second snap ring engaging portion 63a and the second snap ring are engaged. A first snap ring engagement portion 36a facing the ring engagement portion 63a is formed to be inclined with respect to each other. Thereby, when a load in a direction in which the shaft 60 is pulled out from the inner member 30 is applied, only a part of the second snap ring engaging portion 63 a presses the snap ring 70.

  That is, only a part of the snap ring 70 in the circumferential direction is pressed by the second snap ring engaging part 63a, and the other part of the snap ring 70 is not pressed by the second snap ring engaging part 63a. For this reason, a load in the reduced diameter direction is applied only to a part of the snap ring 70 in the circumferential direction. Even if a load in the reduced diameter direction is applied to a part of the circumferential direction of the snap ring 70, no load in the reduced diameter direction is applied to the other parts at all. The snap ring 70 is not reduced in diameter only by moving in the direction in which a load is applied along the two snap ring recesses 63. Further, even if a load in the diameter reducing direction is applied to a part of the circumferential direction of the snap ring 70, the opening end 70b of the snap ring 70 is an intersection of the inclined second snap ring recess 63. The snap ring 70 is prevented from being reduced in diameter by being caught by the male spline 62. Thus, the diameter reduction of the snap ring 70 is reliably prevented, so that the shaft 60 can be reliably prevented from coming off from the insertion hole 34 of the inner member 30.

  In the above-described embodiment, both the second snap ring engagement portion 63a and the central side surface 63b are inclined with respect to the surface b perpendicular to the axis a of the shaft 60. However, the second snap ring engagement portion Even if only 63a is inclined with respect to the plane B orthogonal to the axis A of the shaft 60, there is no problem.

  The second snap ring engagement portion 63a is formed in parallel with the surface B orthogonal to the axis A of the shaft 60, while the first snap ring engagement facing the second snap ring engagement portion 63a. There is no problem even in an embodiment in which the portion 36a is inclined with respect to the surface b orthogonal to the axis a of the inner member 30. Alternatively, the second snap ring engaging portion 63a is formed to be inclined with respect to the surface B orthogonal to the axis A of the shaft 60, and the first snap ring engaging portion 36a is also orthogonal to the axis a of the inner member 30. The first snap ring engaging portion 36a and the second snap ring engaging portion 63a may be inclined with respect to the surface b to be inclined, and the first snap ring engaging portion 36a and the second snap ring engaging portion 63a may be inclined. Even in such an embodiment, only a part of the second snap ring engaging portion 63a presses the snap ring 70 when a load is applied to the shaft 60 in the direction of being pulled out from the inner member 30. Only the part of the snap ring 70 in the circumferential direction is pressed by the second snap ring engaging portion 63a. For this reason, since the diameter reduction of the snap ring 70 is reliably prevented as in the above-described embodiment, the shaft 60 can be reliably prevented from coming off from the insertion hole 34 of the inner member 30.

  In the above-described embodiment, the ball-type constant velocity joint 10 is provided between the outer ring 20 and the inner member 30 and uses the ball 40 as a torque transmission member that transmits torque between the outer ring 20 and the inner member 30. The constant velocity joint of the invention has been described. The torque transmission member is not limited to the ball 40, and is rotatably attached to three pins formed on the inner member 30, and slidably engages with a roller groove formed on the inner peripheral surface of the outer ring 20. Even rollers can be used. Such a constant velocity joint, that is, a tripod type constant velocity joint, can be applied to a structure capable of preventing the shaft from coming off from the insertion hole of the inner member, which is the technical idea of the present invention. Needless to say.

DESCRIPTION OF SYMBOLS 10 ... Constant velocity joint 20 ... Outer ring, 21 ... Connecting shaft, 23 ... Outer ring ball groove 30 ... Inner member, 34 ... Insertion hole 35 ... Female spline, 36 ... 1st snap ring recessed part, 36a ... 1st snap ring engaging part 40 ... Ball (torque transmission member)
DESCRIPTION OF SYMBOLS 50 ... Cage, 53 ... Window part 60 ... Shaft, 61 ... Fitting part, 62 ... Male spline, 63 ... 2nd snap ring recessed part, 63a ... 2nd snap ring engaging part 70 ... Snap ring, 70a ... Notch part 70b ... open end A ... shaft axis, B ... plane perpendicular to the axis of the shaft a ... axis of the inner member, b ... plane perpendicular to the axis of the inner member

Claims (1)

An outer ring formed in a bottomed cylindrical shape,
An inner member that is disposed inside the outer ring so as to be able to swing relative to the outer ring and has an insertion hole;
A plurality of torque transmission members that are disposed between the outer ring and the inner member and engage the outer ring and the inner member to transmit torque between the outer ring and the inner member;
A shaft where a fitting portion is formed on the outer peripheral surface on the front end side, the fitting portion is inserted through the insertion hole and connected to the inner member;
A C-shaped snap ring that engages in the axial direction with respect to the insertion hole and the fitting portion, and prevents the shaft from coming off from the inner member;
With
A plurality of female splines are formed along the axial direction of the inner member on the inner peripheral surface of the insertion hole of the inner member, and a first snap ring engaging portion is formed so as to cross the female spline. ,
A plurality of male splines are formed along the axial direction of the shaft on the outer peripheral surface of the fitting portion of the shaft, and a second snap ring engaging portion is formed so as to cross the male spline.
The male spline is engaged with the female spline, the snap ring is engaged with the first snap ring engaging portion and the second snap ring engaging portion facing each other, and the shaft is connected to the inner member. Connected to non-rotatable relative to
The constant velocity joint, wherein the first snap ring engaging portion and the second snap ring engaging portion are inclined to each other.

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