JP2009014036A - Cross groove type constant velocity universal joint - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a cross groove type constant-velocity universal joint capable of reducing the weight and size while increasing the number of balls without impairing the function of the constant-velocity universal joint. <P>SOLUTION: Ten balls 4 are incorporated in a crossing part of a track groove 7 of an outer ring 2 and a track groove 8 of an inner ring 8. A value obtained by dividing PCD of a virtual circle C connecting centers of the ten balls 4 by the diameter ϕD of the ball 4 is set to 4.3-4.8. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a cross-groove type constant velocity universal joint which is one of sliding type constant velocity universal joints used for driving shafts of automobiles and various industrial machines.

  The propeller shaft used in 4WD vehicles (four-wheel drive vehicles) and FR (rear wheel drive vehicles with the engine disposed at the front of the vehicle body) is located between the transmission (transmission device) and the differential (actuating gear device). The cross groove type constant velocity universal joint is provided in order to obtain a structure that can cope with the relative position change.

  Cross groove type constant velocity universal joints are roughly classified into two types: a float type and a non-float type. Both types of constant velocity universal joints are selectively used according to the characteristics of the vehicle equipped with the propeller shaft (the amount of axial displacement of the constant velocity universal joint, the load capacity, etc.).

  8 to 11 illustrate a conventional float type cross groove type constant velocity universal joint.

  As shown in FIG. 8, the constant velocity universal joint 101 includes an outer ring 102 that is an outer joint member having openings at both ends, and an internal component 106 disposed inside the outer ring 102. The internal part 106 includes an inner ring 103, a ball 104, and a cage 105, which are inner joint members. The float type cross groove type constant velocity universal joint 101 is formed such that the maximum outer diameter A of the inner ring 103 is larger than the minimum inner diameter B of the cage 105.

  The outer ring 102 has a plurality of linear track grooves 107 formed on the inner peripheral surface, and the inner ring 103 has a plurality of linear track grooves 108 formed on the outer peripheral surface. A center hole 111 is formed at the center of the inner ring 103, and a stub shaft 112 is inserted into the center hole 111. 9 shows a front view of the outer ring 102 and the inner ring 103 shown in FIG.

  FIG. 10 shows a partial front view of the track grooves (107, 108) formed in the outer ring 102 and the inner ring 103. As shown in the figure, the track groove 107 of the outer ring 102 and the track groove 108 of the inner ring 103 are formed to be inclined with respect to the axis L by the crossing angle α in opposite directions. The ball 104 is incorporated at the intersection of the track groove 107 of the outer ring 102 and the track groove 108 of the inner ring 103, and this ball 104 is held in a pocket 109 of the cage 105 as shown in FIG.

  As shown in FIG. 11, the cross-sectional shapes of the track groove 107 of the outer ring 102 and the track groove 108 of the inner ring 103 are formed in a Gothic arch shape by broaching or the like with a radius of curvature larger than that of the ball 104. For this reason, the track groove 107 of the outer ring 102 and the track groove 108 of the inner ring 103 are in contact with the ball 104 at two points as shown by P in the drawing, and are in angular contact with a ball contact angle β. . The ball contact angle β is based on the center O of the ball 104 and the ball contact center P where the ball 103 and the track grooves (107, 108) are in contact with the groove bottom center Q of the track grooves (107, 108). Means the angle between

  An end plate 110 for preventing leakage of grease filled in the joint and preventing entry of foreign matters is attached to one open end of the outer ring 102. On the other hand, a sealing device is attached to the other opening end of the outer ring 102.

  This sealing device includes a boot 113 and a metal boot adapter 120. The boot 113 has a U-shaped cross section having a large-diameter end portion 114 and a small-diameter end portion 115, and the small-diameter end portion 115 is attached to the outer peripheral surface of the stub shaft 112. It is fixed by crimping.

  The boot adapter 120 has a cylindrical shape, and one end 116 is attached to the outer peripheral surface of the outer ring 102, and is fixed together with the above-described end plate 110 by bolting (not shown) from the insertion side of the stub shaft 112. The other end 117 is fixed by crimping to the large-diameter end 114 of the boot 113. The stub shaft 112 is prevented from coming off by a snap ring 119 at the opening on the end plate 110 side of the inner ring 103.

  In the constant velocity universal joint 101 as described above, it is known that the number of balls 104 is four or more (generally six), and FIG. 9 illustrates the case of six balls. Yes. The crossing angle α with respect to the axis L of the track groove 107 of the outer ring 102 and the track groove 108 of the inner ring 103 shown in FIG. 10 is parallel to the track grooves (107, 108) when the constant velocity universal joint takes the maximum operating angle. It is designed to be an angle (generally 13 to 19 °). Further, the groove diameters of the opposing track grooves (107, 108) are 1.01-1.04 times the diameter of the ball 104, and the ball contact angle β shown in FIG. 11 is 30-45 ° ( Non-patent document 1).

  Incidentally, as means for ensuring the sliding stroke of the cross groove type constant velocity universal joint 101 as shown in FIG. 8 (the axially movable region of the internal part 106), the track grooves of the outer ring 102 and the inner ring 103 shown in FIG. It is known to reduce the crossing angle α of (107, 108).

  However, if the crossing angle α of the track grooves (107, 108) is reduced, there is a problem that the maximum operating angle of the constant velocity universal joint 101 is reduced. Here, the maximum operating angle is an angle at which a phenomenon occurs in which excessive torque acts when an operation of returning the joint after it is bent without rotating is performed. When such a phenomenon occurs, in some cases, a phenomenon occurs in which the joint cannot be returned with an angle and is caught. Such a situation becomes a problem at the time of assembling the constant velocity universal joint to the automobile. For this reason, when assembling the constant velocity universal joint 101 to the automobile, it is necessary to return the joint after bending it once. It is to become. For this reason, in the constant velocity universal joint, the operating angle is small, and when the joint is bent and returned later, the workability of assembling the constant velocity universal joint to the automobile is lowered.

  Further, the cross groove type constant velocity universal joint 101 as shown in FIG. 8 is mainly applied to the ball 104 from the track groove 107 of the outer ring 102 at the intersection of the track grooves (107, 108) when the operating angle is taken. The direction of the resultant force of the load and the frictional force generated when the ball 104 rolls on the track groove 107 of the outer ring 102, the main load applied to the ball 104 from the track groove 108 of the inner ring 103, and the track groove 108 of the inner ring 103. The wedge angle is formed by the direction of the resultant force of the frictional force generated by rolling.

  Due to the wedge angle, the ball 104 is pushed into the pocket 109 of the cage 105 in an attempt to jump out from the intersection of the track grooves (107, 108). Here, in the cross groove type constant velocity universal joint as shown in FIG. 8, as already described, the track groove 107 of the outer ring 102 and the track groove 108 of the inner ring 103 are inclined in opposite directions with respect to the axis. Therefore, the adjacent balls 104 try to jump out from the intersections in the opposite direction. As a result, the cage 105 is positioned by the ball 104, and the intersection of the track grooves (107, 108) is always located on the bisector of the operating angle, so that the ball 104 is always in the track groove (107 108) and maintained on the bisector of the operating angle. For this reason, the cross groove type constant velocity universal joint has a constant velocity and a structure with little backlash.

  However, the wedge angle has a limit angle that reverses when the constant velocity universal joint 101 takes the operating angle (the wedge angle exceeds 180 °). It has been found that this limit angle is determined by the crossing angle α shown in FIG. 10 and the contact angle β shown in FIG. When the constant velocity universal joint 101 takes a large operating angle, if the wedge angle takes the limit angle and reverses, the balance of the force acting on the cage 105 from the ball 104 is lost. As a result, the cage 105 cannot be balanced in force and becomes unstable.

  As a technique for solving the above problem, a technique is known in which the number of balls 104 is set to 10 more than the case of 6 balls shown in FIG. 6 and the crossing angle α is set to 10 to 15 ° ( Patent Document 1).

This constant velocity universal joint stabilizes the driving of the cage 105 even when a large operating angle is taken. This is because the driving force of the balls 104 accommodated in the intersections of the track grooves (7, 8) whose wedge angles are reversed is shared by the other balls 104 to stabilize the driving of the cage 105. In the above case, the crossing angle α of the track grooves (107, 108) can be designed to be as small as 10 to 15 °, so that the sliding stroke of the constant velocity universal joint 101 can be ensured.
Universal Joint and Driveshaft Design Manual Section 3.2.12 “Cross Groove Universal Joint” JP 2006-266423 A

  Now, according to the technique described in the above-mentioned Patent Document 1, in the cross groove type constant velocity universal joint, the number of balls is 10 and the crossing angle α between the track groove of the outer ring and the track groove of the inner ring is By setting the angle to 10 to 15 °, the maximum operating angle of the constant velocity universal joint can be increased and the sliding stroke can be secured. In addition, the constant velocity universal joint can be reduced in weight and size.

  However, in the invention described in Patent Document 1, in order to set the number of balls to 10, the ball diameter (ball diameter) must be reduced, and accordingly, the outer ring and the inner ring are formed. The groove diameter of the track groove must also be reduced. As a result, there has been a concern that the ball may come off the track groove when the constant velocity universal joint is operated.

  The present invention has been made in view of the above circumstances, and is capable of increasing the number of balls to reduce the weight and size without compromising the function of the constant velocity universal joint. The object is to provide a joint.

  As one of the cross-groove type constant velocity universal joints of the present invention for solving the above-mentioned problems, an outer joint member in which a plurality of linear track grooves inclined with respect to the axis are formed on the inner peripheral surface, and an outer periphery An inner joint member having a surface formed with a track groove inclined in a direction opposite to the track groove of the outer joint member with respect to the axis, and an intersection of the track groove of the outer joint member and the track groove of the inner joint member A lower limit of a value obtained by dividing a PCD of a virtual circle connecting the centers of the balls by a ball diameter, including a plurality of incorporated balls and a cage that holds the balls between the outer joint member and the inner joint member The value is 4.3.

  When the PCD, which is the diameter of a virtual circle connecting the centers of a plurality of balls held in the cage, divided by the ball diameter (ball diameter) is less than 4.3, the PCD of the virtual circle is excessive compared to the ball diameter The track grooves formed in the outer joint member and the inner joint member interfere with each other on the end surfaces of the outer joint member and the inner joint member, thereby impairing the function as a constant velocity universal joint. Become. Therefore, it is effective that the lower limit of the value obtained by dividing the virtual circle PCD by the ball diameter is 4.3.

  Moreover, as a second cross-groove type constant velocity universal joint for solving the above-mentioned problems, an outer joint member in which a plurality of linear track grooves inclined with respect to the axis are formed on the inner peripheral surface, and the outer peripheral surface And an inner joint member formed with a track groove inclined in a direction opposite to the track groove of the outer joint member with respect to the axis, and a cross groove portion between the track groove of the outer joint member and the track groove of the inner joint member. An upper limit of a value obtained by dividing the PCD of a virtual circle connecting the centers of the balls by the ball diameter, and a cage that holds the balls between the outer joint member and the inner joint member Is 4.8.

  This is because when the value obtained by dividing the virtual circle PCD by the ball diameter is larger than 4.8, the virtual circle PCD is excessively larger than the ball diameter. In this case, the outer diameter of the outer joint member increases, and the constant velocity universal joint increases in size and increases in weight. Also, the track grooves formed in the outer joint member and the inner joint member become shallow, and the ball is tracked. There is a possibility of getting off the groove. Therefore, it is effective that the upper limit of the value obtained by dividing the virtual circle PCD by the ball diameter is 4.8.

  Alternatively, as a third cross groove type constant velocity universal joint for solving the above problems, an outer joint member in which a plurality of linear track grooves inclined with respect to the axis line are formed on the inner peripheral surface, and the outer peripheral surface And an inner joint member formed with a track groove inclined in a direction opposite to the track groove of the outer joint member with respect to the axis, and a cross groove portion between the track groove of the outer joint member and the track groove of the inner joint member. And a cage for holding the ball between the outer joint member and the inner joint member, and a value obtained by dividing the virtual circle PCD connecting the centers of the balls by the ball diameter is 4. It is characterized by being 3 or more and 4.8 or less.

  When the value obtained by dividing the PCD of the virtual circle by the ball diameter is smaller than 4.3, as described above, the track grooves formed in the outer joint member and the inner joint member are adjacent to each other in the outer joint. When the value obtained by dividing the PCD of the virtual circle by the ball diameter is larger than 4.8, it interferes with the respective end faces of the member and the inner joint member, thereby impairing the function as a constant velocity universal joint. The outer diameter of the outer joint member becomes larger, the constant velocity universal joint becomes larger and the weight increases, and the track grooves formed on the outer joint member and the inner joint member become shallower, and the ball rides on the track groove. This is because there is a possibility that it will fall off. Therefore, it is effective that the value obtained by dividing the virtual circle PCD by the ball diameter is 4.3 to 4.8.

  The three inventions described above are cross-groove type constant velocity universal joints called float types in which the maximum outer diameter of the inner joint member is larger than the minimum inner diameter of the cage, and the maximum outer diameter of the inner joint member is larger than the minimum inner diameter of the cage. It can be applied to a cross-bulb type constant velocity universal joint called a reduced non-float type. In addition, the non-float type cross groove type constant velocity universal joint can secure the axially movable region of the inner joint member as compared with the float type cross groove type constant velocity universal joint.

  In the inventions mentioned so far, the number of balls is preferably 10.

  When the constant velocity universal joint has a large operating angle, the main load applied to the ball from the track groove of the outer joint member and the ball is applied to the outer joint member at the intersection of the track groove of the outer joint member and the track groove of the inner joint member. Direction of the friction force generated by rolling the track groove of the inner joint, the main load applied to the ball from the track groove of the inner joint member, and the friction force generated by the ball rolling on the track groove of the inner joint member Inversion occurs in the wedge angle formed by the direction of the resultant force, and the driving of the cage becomes unstable. However, as in the present invention described above, by setting the number of balls to ten, the other balls share the driving force of the balls accommodated in the crossing portion where the wedge angle is reversed. Driving can be stabilized.

  According to the cross groove type constant velocity universal joint of the present invention, the lower limit value of the value obtained by dividing the PCD of the virtual circle connecting the centers of the plurality of balls by the ball diameter is 4.3, or the upper limit value is 4.8. By doing so, the number of balls can be increased and the constant velocity universal joint can be reduced in weight and size without impairing the function of the constant velocity universal joint.

  Embodiments of the present invention will be described below with reference to the accompanying drawings.

  FIG. 1 shows a first embodiment of the present invention.

  FIG. 1 shows a float type cross groove type constant velocity universal joint. The constant velocity universal joint 1 includes an outer ring 2 that is an outer joint member having openings at both ends, and an internal component 6 disposed inside the outer ring 2. The internal component 6 is composed of an inner ring 3, a ball 4, and a cage 5 that are inner joint members. In this float type cross groove type constant velocity universal joint, the maximum outer diameter A of the inner ring 3 is formed larger than the minimum inner diameter B of the cage 5 as shown in FIG. 2 shows a partial front view of the outer ring 2 and the inner ring 3 of FIG.

  The outer ring 2 has a plurality of linear track grooves 7 formed on the inner peripheral surface, and the inner ring 3 has a plurality of linear track grooves 8 formed on the outer peripheral surface. A center hole 11 is formed at the center of the inner ring 3, and a stub shaft 12 is inserted into the center hole 11.

  FIG. 3 shows a partial front view of the track grooves (7, 8) formed in the outer ring 2 and the inner ring 3. As shown in the figure, the track groove 7 of the outer ring 2 and the track groove 8 of the inner ring 3 are formed to be inclined with respect to the axis L by a crossing angle α in opposite directions. The ball 4 is incorporated at the intersection of the track groove 7 of the outer ring 2 and the track groove 8 of the inner ring 3, and this ball 4 is held in a pocket 9 of a cage 5 as shown in FIG.

  As shown in FIG. 4, the cross-sectional shapes of the track groove 7 of the outer ring 2 and the track groove 8 of the inner ring 3 are formed in a Gothic arch shape by broaching or the like with a radius of curvature larger than that of the ball 4. Therefore, the track groove 7 of the outer ring 2 and the track groove 8 of the inner ring 3 are in contact with the ball 4 at two points as shown by P in the figure, and are in angular contact with a ball contact angle β. . The ball contact angle β is based on the center O of the ball 4 and the ball contact center P where the ball 3 contacts the track grooves (7, 8) and the groove bottom center Q of the track grooves (7, 8). Means the angle between

  As shown in FIG. 1, an end plate 10 for preventing leakage of grease filled in the joint and preventing entry of foreign matters is attached to one open end of the outer ring 2. On the other hand, a sealing device is attached to the other opening end of the outer ring 1.

  The sealing device includes a boot 13 and a metal boot adapter 20. The boot 13 has a U-shaped cross section having a large-diameter end 14 and a small-diameter end 15, and the small-diameter end 15 is attached to the outer peripheral surface of the stub shaft 12. It is fixed by crimping.

  The boot adapter 20 has a cylindrical shape, and one end portion 16 is attached to the outer peripheral surface of the outer ring 2, and is fixed together with the above-described end plate 10 by bolting (not shown) from the insertion side of the stub shaft 12. The other end 17 is fixed by crimping to the large-diameter end 14 of the boot 13. The stub shaft 12 is prevented from coming off by a snap ring 19 at the opening of the inner ring 3 on the end plate 10 side.

  In the present embodiment, as shown in FIG. 2, the number of balls 4 is set to 10 as compared with the conventional case of 6 pieces (see FIG. 9), and the track groove of the outer ring 2 shown in FIG. 7 and the crossing angle α with respect to the axis L of the track groove 8 of the inner ring 3 is 10 to 15 °.

  When the number of balls is 6 or less, when the constant velocity universal joint takes the maximum operating angle, at the intersection (see FIGS. 3 and 4) of the track grooves (7, 8) of the outer ring 2 and the inner ring 3 The direction of the resultant force of the main load applied to the ball 4 from the track groove 7 of the outer ring 2 and the frictional force generated when the ball 4 rolls on the track groove 7 of the outer ring 2, and the direction of the resultant force from the track groove 8 of the inner ring 3 to the ball 4 The wedge angle formed by the main load and the direction of the resultant force of the frictional force generated when the ball 4 rolls on the track groove 8 of the inner ring 3 is reversed at the limit angle.

  The limit angle is determined by the crossing angle α of the track grooves (7, 8) shown in FIG. 3 and the contact angle β between the ball 4 and the track grooves (7, 8) shown in FIG. Here, the contact angle β is based on the center O of the ball 4 and the ball contact center P where the ball 3 contacts the track groove (7, 8) and the groove bottom center Q of the track groove (7, 8). Means the angle between

  As described above, when the wedge angle takes the limit angle and reverses, the balance of the force acting on the cage 5 from the ball 4 is lost. As a result, the cage 5 cannot be balanced in force and becomes unstable.

  However, in the present embodiment, the driving of the cage 5 can be stabilized by setting the number of the balls 4 to ten. This is because the other balls 4 share the driving force of the balls 4 accommodated in the intersections of the track grooves (7, 8) whose wedge angles have been reversed. In addition, by setting the number of balls to 10, the crossing angle α of the track grooves (7, 8) can be designed as small as 10 to 15 °, so that the sliding stroke of the constant velocity universal joint 1 can be secured. it can.

  Further, in the present embodiment, as shown in FIG. 2, the PCD, which is the diameter of a virtual circle C connecting the centers of the ten balls interposed at the intersections of the track grooves (7, 8), is set to the diameter of the ball 4 ( It is desirable that the value obtained by dividing the diameter of the ball 4 by φD is 4.3 or more and 4.8 or less. This is due to the following two reasons.

  As a first reason, when PCD / φD is smaller than 4.3, the PCD of the virtual circle C is excessively smaller than the diameter φD of the ball 4. This is caused by making the PCD of the virtual circle C excessively smaller than the diameter φD of the ball 4 or making the diameter φD of the ball 4 excessively larger than the PCD of the virtual circle C. In this case, as shown in FIG. 5, adjacent track grooves (7, 8) formed in the outer ring 2 and the inner ring 3 interfere with each other on the end faces of the outer ring 2 and the inner ring 3. As a result, the function of the constant velocity universal joint 1 is impaired. In FIG. 5, in order to make the drawing easier to see, the inner ring 3 shown in FIG. 1 and the track groove 8 formed in the inner ring 3 are not shown.

  As a second reason, when PCD / φD is larger than 4.8, the PCD of the virtual circle C is excessively larger than the diameter φD of the ball 4. This is caused by making the PCD of the virtual circle C excessively larger than the diameter φD of the ball 4 or making the diameter φD of the ball 4 excessively smaller than the PCD of the virtual circle C. In this case, the outer ring 2 is formed with a larger outer diameter, or the track grooves (7, 8) formed in the outer ring 2 and the inner ring 3 are formed shallow. However, as shown in FIG. 6, when the outer diameter of the outer ring 2 is increased, the constant velocity universal joint 1 is increased in size and weight, and the track grooves (7, 8) formed in the outer ring 2 and the inner ring 3 are caused. Is formed shallowly, there is a possibility that the ball 4 rides on the track grooves (7, 8) and comes off. In FIG. 6, in order to make the drawing easier to see, the illustration of the inner ring 3 shown in FIG. 1 and the track groove 8 formed thereon is omitted.

  In the case of the constant velocity universal joint 1 of the present embodiment, the track groove (7, 8) generated by reducing the crossing angle α of the track groove (7, 8) shown in FIG. 3 in order to ensure the sliding stroke. Inversion of the wedge angle formed at the crossing portion of the outer ring 1 can be prevented, and the number of balls 4 can be increased to reduce the outer diameter of the outer ring 1 in order to reduce the weight and size of the constant velocity universal joint 1. The function of the constant velocity universal joint 1 is not impaired.

  In the present embodiment, the number of balls is ten. However, when the number of balls of the constant velocity universal joint 1 is larger than the conventional six (see FIG. 9), the number of balls 4 is eight. You can also

  Thus, when the number of the balls 4 is 8, the outer diameter of the outer ring 2 is the same as that of the case where the number of the balls 4 is 10 as described above, and is a conventional constant velocity universal joint having 6 balls. Since the outer diameter of the outer ring (see FIG. 9) can be made smaller, the constant velocity universal joint 1 can be reduced in weight and size. However, when the number of balls 4 is eight, the pair of track grooves 7 corresponding to the diameter direction formed in the outer ring 2 and the pair of track grooves 8 corresponding to the diameter direction formed in the inner ring 3 are opposite to each other. In this case, the pair of track grooves 7 of the outer ring 2 and the pair of tracks 8 of the inner ring 3 cannot be processed simultaneously. Therefore, workability of the outer ring 2 and the inner ring 3 is deteriorated.

  However, if the number of balls is 10 as in this embodiment, the pair of track grooves 7 corresponding to the diameter direction formed in the outer ring 2 and the pair of track grooves 8 corresponding to the diameter direction formed in the inner ring 3 are Since the inclined directions are the same, the pair of track grooves 7 of the outer ring 2 and the pair of tracks 8 of the inner ring 3 can be processed simultaneously. Therefore, the workability of the outer ring 2 and the inner ring 3 is good.

  The present invention can also be applied to the non-float type cross groove constant velocity universal joint shown in FIG. The basic structure of this constant velocity universal joint is the same as that of the float type cross groove type constant velocity universal joint 1 shown in FIG. 1, and 30 is added to the reference numerals attached to the respective portions in FIG. The code | symbol is attached | subjected.

  The non-float type cross groove constant velocity universal joint 31 according to the second embodiment of the present invention is designed such that the maximum outer diameter A of the inner ring 33 is smaller than the minimum inner diameter B of the cage 35.

  With the above-described structure, when the internal component 36 moves in the axial direction toward the boot 43, the constant velocity universal joint 31 is restricted from moving in the axial direction due to the balls 34 and the boot adapter 50 interfering with each other. When moving in the axial direction, the ball 34 and the pocket 39 of the cage 35 interfere with each other, and the axial movement is restricted. In this case, the axially movable region of the internal component 36 is larger than the float type cross groove type constant velocity universal joint shown in FIG.

  The reason for this is that in the float-type cross-groove constant velocity universal joint shown in FIG. 1, when the internal part 6 moves to the boot 13 side, the inner ring 3 and the cage 5 interfere with each other to restrict axial movement. Even when the internal part 6 moves in the axial direction toward the end plate 10, the inner ring 3 and the cage 5 interfere with each other and the axial movement is restricted. However, each interference is more than in the case of the non-float type shown in FIG. This is because interference occurs early.

  The embodiments of the present invention have been described above. However, these are merely examples, and various modifications can be made within the meaning and content of the claims.

  For example, in the embodiment mentioned here, the present invention is applied to a cross groove type constant velocity universal joint whose outer ring shape is a disk type. However, the present invention is not limited to this, and the outer ring shape is a flange type or bell type. The present invention can also be applied to a cross groove type constant velocity universal joint.

It is sectional drawing which shows the float type cross groove type constant velocity universal joint which is the 1st Embodiment of this invention. It is a front view explaining PCD of the ball center shown in FIG. FIG. 2 is a partial front view of track grooves formed in an outer ring and an inner ring shown in FIG. 1. It is a partial front view for demonstrating the contact angle of the track groove | channel formed in the outer ring | wheel and the inner ring | wheel, and the ball interposed in these crossing parts. It is a front view explaining the case where the value which divided PCD of the virtual circle shown in FIG. 2 by the diameter φD of the ball is smaller than 4.3. FIG. 6 is a front view for explaining a case where a value obtained by dividing the PCD of the virtual circle shown in FIG. The 2nd Embodiment of this invention is shown and it is sectional drawing which applied this invention to the non-float type cross groove type constant velocity universal joint. It is sectional drawing which shows the conventional non-float type cross groove type constant velocity universal joint. FIG. 10 is a front view of the outer ring and the inner ring shown in FIG. 9. It is a partial front view of the track groove formed in the outer ring and the inner ring shown in FIG. It is a partial front view for demonstrating the contact angle of the track groove | channel formed in the outer ring | wheel and the inner ring | wheel shown in FIG. 8, and the ball interposed in these crossing parts.

Explanation of symbols

1,31 Sliding type constant velocity universal joint (LJ)
2, 32 Outer ring (outer joint member)
3, 33 Inner ring (inner joint member)
4, 34 Ball 5, 35 Cage 6, 36 Internal parts 7, 37 Track groove (outer ring)
8, 38 Track groove (inner ring)
α Cross angle β Contact angle C Virtual circle of the ball

Claims (6)

An outer joint member formed with a plurality of linear track grooves inclined with respect to the axis on the inner peripheral surface, and a track groove inclined with a direction opposite to the track grooves of the outer joint member with respect to the axis are formed on the outer peripheral surface. The inner joint member, a plurality of balls incorporated in a crossing portion of the track groove of the outer joint member and the track groove of the inner joint member, and the ball between the outer joint member and the inner joint member. A holding cage,
A cross groove type constant velocity universal joint, wherein a lower limit value of a value obtained by dividing the PCD of a virtual circle connecting the centers of the balls by the ball diameter is 4.3. An outer joint member formed with a plurality of linear track grooves inclined with respect to the axis on the inner peripheral surface, and a track groove inclined with a direction opposite to the track grooves of the outer joint member with respect to the axis are formed on the outer peripheral surface. The inner joint member, a plurality of balls incorporated in a crossing portion of the track groove of the outer joint member and the track groove of the inner joint member, and the ball between the outer joint member and the inner joint member. A holding cage,
A cross groove type constant velocity universal joint characterized in that an upper limit of a value obtained by dividing the PCD of a virtual circle connecting the centers of the balls by the ball diameter is 4.8. An outer joint member formed with a plurality of linear track grooves inclined with respect to the axis on the inner peripheral surface, and a track groove inclined with a direction opposite to the track grooves of the outer joint member with respect to the axis are formed on the outer peripheral surface. The inner joint member, a plurality of balls incorporated in a crossing portion of the track groove of the outer joint member and the track groove of the inner joint member, and the ball between the outer joint member and the inner joint member. A holding cage,
A cross-groove type constant velocity universal joint characterized in that a value obtained by dividing PCD of a virtual circle connecting the centers of the balls by the ball diameter is 4.3 or more and 4.8 or less.   The cross groove type constant velocity universal joint according to any one of claims 1 to 3, wherein a maximum outer diameter of the inner joint member is larger than a minimum inner diameter of the cage.   The cross groove type constant velocity universal joint according to any one of claims 1 to 3, wherein a maximum outer diameter of the inner joint member is smaller than a minimum inner diameter of the cage.   The cross-groove type constant velocity universal joint according to any one of claims 1 to 5, wherein the number of balls is ten.

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