JP2006258207A - Fixed type constant velocity universal joint - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To reduce heat quantity during rotation of a constant velocity universal joint without following cost increase due to coating treatment or improvement of grease. <P>SOLUTION: In this fixed type constant velocity universal joint, either or both of a pocket gap or a spherical surface gap between an inner ring and a cage are set in the optimum size among inner design specifications. For the pocket gap, an axial gap between a pocket 46 and a ball 30 is set in a range of 0 to +0.030 mm. For the spherical gap between the inner ring and the cage, a gap ratio of the spherical gap between the inner ring 20 and the cage 40 is set in a range of 0.60 to 2.60. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a fixed type constant velocity universal joint. A constant velocity universal joint is a power transmission system for automobiles and various industrial machines that transmits torque at a constant angular speed by connecting the rotating shaft on the drive side and the rotating shaft on the driven side. The slidable type allows angular displacement and axial displacement, whereas the fixed type allows only angular displacement.

  The fixed type constant velocity universal joint has a structure that can give only an angle. In the case of a drive shaft for an automobile, the angle includes a normal angle determined by the layout of the tire and the differential gear when the vehicle is mounted, and the handle There is a steering angle that changes with steering. In recent years, with the diversification of vehicle layout, a constant velocity universal joint that can withstand use at a high common angle is required.

  However, as the service angle increases, the temperature rise of the constant velocity universal joint itself increases accordingly. In addition, the constant velocity universal joint used for the propeller shaft is used in a very high rotation range as compared with the drive shaft, so that the temperature rise due to heat generation is severe. The temperature increase of the constant velocity universal joint causes deterioration of the grease, a decrease in the life of the constant velocity universal joint due to a change in heat treatment status (decrease in surface hardness, etc.), and deformation and breakage of the boot due to expansion of internal air.

The temperature rise of the ball type constant velocity universal joint is caused by the heat generated by the friction force generated by the contact between the ball and the ball groove of the outer ring and the ball groove of the inner ring, the contact between the ball and the cage, and the spherical contact between the cage and the outer ring and the inner ring. to cause. Conventionally, as a method of suppressing this temperature rise, the frictional force is reduced by coating the cage, the outer ring, or the inner ring with a material having excellent friction performance (Patent Document 1, Patent Document 2), or a lower friction. In general, grease is used, and a method for reducing heat generation by suppressing friction by optimizing the internal dimensional accuracy is as specified in Patent Document 3 for the contact angle.
JP 2000-46061 A JP 2000-145804 A JP-A-8-128454

  When the constant velocity universal joint rotates at an angle, heat is generated, and this heat generation causes deformation of the boot due to the decrease in the life of the constant velocity universal joint and the expansion of the internal air due to the temperature rise. The boot may be damaged. The conventional measures taken to suppress this heat generation are disadvantageous in terms of processing time and cost, and cannot be used inexpensively in all constant velocity universal joints. For the same reason, switching to an expensive low friction grease is disadvantageous in terms of cost.

  The main object of the present invention is to reduce the amount of heat generated during the rotation of the constant velocity universal joint without increasing the cost as in the case of coating treatment or improvement of grease.

  The present invention solves the problem by setting the pocket clearance or the inner ring / cage spherical clearance or both to the optimum dimensions in the internal design specifications of the fixed type constant velocity universal joint.

In other words, the fixed type constant velocity universal joint according to claim 1 includes a plurality of ball grooves extending in the axial direction formed on the inner spherical surface at equal intervals in the circumferential direction, and an outer ring coupled to the first rotating shaft so as to be able to transmit torque, A plurality of ball grooves extending in the direction are formed on the outer spherical surface at equal intervals in the circumferential direction, and are interposed between the inner ring coupled to the second rotary shaft so as to be able to transmit torque, and between the ball groove of the outer ring and the ball groove of the inner ring. A plurality of balls for transmitting torque, and a cage in which pockets for accommodating the balls are arranged in the circumferential direction;
The center of the ball groove of the outer joint member is offset from the spherical center of the inner spherical surface, and the center of the ball groove of the inner joint member is offset to the opposite side by an equal distance in the axial direction, respectively. Yes,
The axial clearance between the pocket and the ball is in the range of 0 to +0.030 mm.

  The axial clearance is sometimes called a pocket clearance due to the difference between the axial dimension of the pocket and the diameter of the ball. In addition, since a negative (-) value is given when the interference is given, when the axial clearance is the lower limit value, that is, 0, it means that there is no interference and no clearance.

The fixed type constant velocity universal joint according to claim 2 includes an outer ring that is formed with a plurality of ball grooves extending in the axial direction on the inner spherical surface at equal intervals in the circumferential direction and coupled to the first rotating shaft so as to be able to transmit torque, and in the axial direction. A plurality of extending ball grooves are formed on the outer spherical surface at equal intervals in the circumferential direction, and are interposed between an inner ring that is coupled to the second rotating shaft so as to be able to transmit torque, and a torque is interposed between the ball groove of the outer ring and the ball groove of the inner ring. A plurality of balls to be transmitted and a cage in which pockets for accommodating the balls are arranged in the circumferential direction;
The center of the ball groove of the outer joint member is offset from the spherical center of the inner spherical surface, and the center of the ball groove of the inner joint member is offset to the opposite side by an equal distance in the axial direction, respectively. Yes,
The clearance ratio of the spherical clearance between the inner ring and the cage is in the range of 0.60 to 2.60.

The clearance ratio is obtained by multiplying the spherical clearance (diameter value) between the inner ring and the cage divided by the outer spherical reference diameter of the inner ring by 1000. That is,
Clearance ratio = (D _KI −D _I ) / D × 1000
here,
D _KI : Diameter of inner spherical surface of cage D _I : Diameter of outer spherical surface of inner ring D: Reference diameter of outer spherical surface of inner ring

According to a third aspect of the present invention, there is provided a fixed type constant velocity universal joint, wherein a plurality of ball grooves extending in the axial direction are formed on the inner spherical surface at equal intervals in the circumferential direction, and are coupled to the first rotating shaft so as to be able to transmit torque, A plurality of extending ball grooves are formed on the outer spherical surface at equal intervals in the circumferential direction, and are interposed between an inner ring that is coupled to the second rotating shaft so as to be able to transmit torque, and a torque is interposed between the ball groove of the outer ring and the ball groove of the inner ring. A plurality of balls to be transmitted and a cage in which pockets for accommodating the balls are arranged in the circumferential direction;
The center of the ball groove of the outer joint member is offset from the spherical center of the inner spherical surface, and the center of the ball groove of the inner joint member is offset to the opposite side by an equal distance in the axial direction, respectively. Yes,
The axial clearance between the pocket and the ball is in the range of 0 to +0.030 mm, and the clearance ratio of the spherical clearance between the inner ring and the cage is in the range of 0.60 to 2.60. It is characterized by.

  According to a fourth aspect of the present invention, in the fixed type constant velocity universal joint according to any one of the first to third aspects, the ball groove of the outer ring and the ball groove of the inner ring partially have a straight portion. In the present invention, the center of the ball groove of the outer ring is offset from the spherical center of the inner spherical surface, and the center of the ball groove of the inner ring is offset from the spherical center of the outer spherical surface by the same distance in the axial direction. Fixed constant velocity universal joint (BJ) and outer ring ball groove center at the inner spherical surface center and inner ring ball groove center from the outer spherical surface center at equal distances in the axial direction. This is applicable to both fixed type constant velocity universal joints (UJ) that are offset to the opposite side and provided with straight portions having straight groove bottoms in the ball grooves of the outer ring and the inner ring.

  A fifth aspect of the present invention is the fixed type constant velocity universal joint according to any one of the first to fourth aspects, wherein the fixed type constant velocity universal joint is used for a propeller shaft.

  The invention of claim 6 is characterized in that in the fixed type constant velocity universal joint according to any one of claims 1 to 5, eight balls are used. This type of fixed type constant velocity universal joint using a ball as a torque transmitting element generally uses six balls, but one ball occupies the total load capacity of the joint by using eight balls. Since the hit load ratio is reduced, the ball diameter and the pitch circle diameter can be reduced as compared with the six ball joints having the same spare number. As a result, the outer ring outer diameter can also be reduced.

  According to the present invention, the amount of heat generated during the rotation of the constant velocity universal joint can be reduced without increasing the cost as in the case of coating treatment or improvement of grease. That is, in the internal design of the constant velocity universal joint, the pocket clearance is set in a range of 0 to +0.030 mm (Claim 1), or the inner ring / cage spherical clearance ratio is set to 0.60 or more and 2.60 or less. (Claim 2) or by setting the pocket clearance to a range of 0 to +0.030 mm and the inner ring / cage spherical clearance ratio to a range of 0.60 to 2.60. (Claim 3) The calorific value of the rotating constant velocity universal joint can be reduced.

  Embodiments of the present invention will be described below with reference to the drawings. 1 and 3 show a Rzeppa constant velocity universal joint (BJ) as a typical example of a fixed type constant velocity universal joint, and FIG. 5 shows an undercut-free fixed type constant velocity universal joint (UJ). Since the cross section is common between the BJ type and the UJ type, FIG. 2 shows one cross section. In the drawings, the gap is exaggerated.

  First, a BJ type embodiment shown in FIGS. 1 to 3 will be described. As shown in the figure, the fixed type constant velocity universal joint includes an outer ring 10, an inner ring 20, a ball 30 and a cage 40 as main components.

  The outer ring 10 as an outer joint member is cup-shaped, and a shaft portion 16 for connecting to one of the two shafts to be coupled is formed on the closed end side. The outer ring 10 has a spherical inner peripheral surface, that is, an inner spherical surface 12, and eight curved ball grooves 14 extending in the axial direction are formed on the inner spherical surface 12 at equal intervals in the circumferential direction.

  The inner ring 20 as an inner joint member has a tooth type (serration or spline) 28 for connecting to the other of the two shafts to be coupled, here the shaft 5. The inner ring 20 has a spherical outer peripheral surface, that is, an outer spherical surface 22, and eight curved ball grooves 24 extending in the axial direction are formed at equal intervals in the circumferential direction on the outer spherical surface 22.

  The ball groove 14 of the outer ring 10 and the ball groove 24 of the inner ring 20 make a pair, and one ball 30 as a torque transmitting element is incorporated in each track formed by the pair of ball grooves 14, 24. A total of eight balls 30 are held in the axial direction by the cage 40. The cage 40 has concentric outer and inner spherical surfaces 42, 44. The outer spherical surface 42 is in spherical contact with the inner spherical surface 12 of the outer ring 10, and the inner spherical surface 44 is in spherical contact with the outer spherical surface 22 of the inner ring 20.

  In this embodiment, the centers P and Q of the ball grooves 14 and 24 are offset from the joint center O by an equal distance (PO = QO = F) to the left and right in the axial direction. That is, the center (outer ring track center) P of the ball groove 14 of the outer ring 10 is offset from the spherical center O of the inner spherical surface 12 by the distance PO toward the opening side of the outer ring 10. The center (inner ring track center) Q of the ball groove 24 of the inner ring 20 is offset from the spherical center O of the outer spherical surface 22 by a distance QO to the back side of the outer ring 10.

  The spherical center of the outer spherical surface 42 of the cage 40 and the spherical center of the inner spherical surface 12 of the outer ring 10 that serves as a guide surface for the outer spherical surface 42 of the cage 40 are all coincident with the joint center O. The spherical center of the inner spherical surface 44 of the cage 40 and the spherical center of the outer spherical surface 22 of the inner ring 20 that serves as a guide surface for the inner spherical surface 44 of the cage 40 are all coincident with the joint center O. Therefore, the offset amount (PO = F) of the outer ring 10 is the axial distance between the center P of the ball groove 14 and the joint center O, and the offset amount (QO = F) of the inner ring 20 is the center of the ball groove 24. The axial distance between Q and the joint center O is the same.

The length PO _{3 of the} line connecting the center P of the ball groove 14 of the outer ring 10 and the center O _{3 of the} ball 30 and the length of the line connecting the center Q of the ball groove 24 of the inner ring 20 and the center O _{3 of the} ball 30. QO ₃ are identical and are indicated by the symbol PCR in FIG. Further, as shown in FIG. 3, an angle formed by a line segment connecting the center P of the ball groove 14 of the outer ring 10 and the center O _{3 of the} ball 30 and a line segment connecting the joint center O and the center O _{3 of the} ball 30 is defined. Called the outer ring track offset angle βo, the angle formed by the line connecting the center Q of the ball groove 24 of the inner ring 20 and the center O _{3 of the} ball 30 and the line connecting the joint center O and the center O _{3 of the} ball 30 is the inner ring. If called the track offset angle βi, the outer ring track offset angle βo and the inner ring track offset angle βi are equal.

In the above configuration, one of the two shafts to be coupled is connected to the outer ring 10, and the other is connected to the inner ring 20. When the outer ring 10 and the inner ring 20 make an angle, the ball 30 guided by the cage 40 is maintained in a plane perpendicular to the bisector of the angle formed by the outer / inner rings 10 and 20, and therefore the ball center O _3. The distances PO ₃ and QO ₃ from the center to the ball groove centers P and Q are also equidistant (PO ₃ = QO ₃ = PCR), and the constant velocity of the joint is ensured.

As described above, the offset amount (F = PO = QO) of the ball grooves 14 and 24 is set so that the ratio value R ₁ = F / PCR is in the range of 0.069 ≦ R ₁ ≦ 0.121. This is preferable from the viewpoints of ensuring allowable load torque, ensuring cage strength, ensuring durability, and ensuring operability. In this embodiment, R ₁ = 0.104 (or 0.1038) is set. A typical value of R _{1 in} a fixed type constant velocity universal joint using six balls is 0.14, and R _{1 in} this embodiment is considerably smaller than that of the comparative product.

FIG. 4 is an enlarged view of the main part of FIG. 2, and shows the mutual relationship between the outer ring 10, the inner ring 20 and the ball 30. The ball groove 14 formed on the inner spherical surface 12 of the outer ring 10 has a Gothic arch shape in cross section, and the ball groove 24 formed on the outer spherical surface 22 of the inner ring 20 has a Gothic arch shape in cross section. Therefore, the ball 30 contacts the ball groove 14 of the outer ring 10 at two points C ₁₁ and C ₁₂ and contacts the ball groove 24 of the inner ring 20 at two points C ₂₁ and C ₂₂ . The angle α formed by the contact points C ₁₁ , C ₁₂ , C ₂₁ , C ₂₂ between the center O ₃ of the ball 30 and the ball grooves 14, 24 with respect to the line segment passing through the center O _{3 of the} ball 30 and the joint center O is Contact angle. The contact angles α of the contact points C ₁₁ , C ₁₂ , C ₂₁ , C ₂₂ are all equal and set to 29 ° or more and 40 ° or less. This contact angle α of 29 ° or more and 40 ° or less is 37 ° or more in the conventional undercut free joint (UJ) using 6 balls, fixed constant velocity universal joint (BJ) using 6 balls, etc. Small compared to 45 ° or less. By setting the contact angle α to 29 ° or more, the contact surface pressure between the ball groove and the ball can be suppressed, and durability equal to or higher than that of the conventional product can be obtained.

  Next, FIG. 5 shows a UJ type embodiment. In this embodiment, a straight portion 16 is provided in the ball groove 14 of the outer ring 10, a straight portion 26 is provided in the ball groove 24 of the inner ring 20, and the spherical centers p, There is no difference from the above-described embodiment shown in FIGS. 1 to 4 except that q is offset in the opposite direction by an equal distance f in the axial direction. Accordingly, substantially the same parts or portions are denoted by the same reference symbols throughout the drawings, and redundant description is omitted.

  The UJ type is characterized in that there is no undercut in the ball groove 14 of the outer ring 10 and the ball groove 24 of the inner ring 20 and a structure that can take a larger operating angle than the BJ type. In recent years, the wheelbase may be lengthened from the viewpoint of improving the collision safety of automobiles, but in order to prevent the turning radius of the vehicle from increasing accordingly, the steering angle of the front wheels is increased by increasing the angle of the fixed constant velocity universal joint. There is a need for an increase. This need for higher angles can be met with a UJ type in which the ball groove shape on the opening side of the outer ring is parallel to the axial direction.

Heat generated by the fixed type constant velocity universal joint is generated between the ball 30 during rotation of the joint and the ball groove 14 of the outer ring 10, between the ball 30 and the ball groove 24 of the inner ring 20, between the ball 30 and the cage 40, and the outer ring. This is caused by frictional heat generated by an internal force between the inner ring 20 and the cage 40 between the inner ring 10 and the cage 40. These internal forces are represented by the various internal dimensions shown in FIG. 2 (the axial clearance between the ball 30 and the pocket 46, the spherical clearance between the outer ring 10 and the cage 40, and the spherical surface between the inner ring 20 and the cage 40. Varies depending on the clearance, PCD clearance, track offset, and contact rate (inner ring / outer ring). Here, the PCD clearance means a difference between the pitch circle diameter PCD _OUTER of the ball groove 14 of the outer ring 10 and the pitch circle diameter PCD _INNER of the ball groove 24 of the inner ring 20. The contact ratio refers to the ratio of the values R _T / R _B of the curvature radius R _T of the cross section of the ball grooves 14, 24 to the radius R _B of the ball 30.

Therefore, to investigate which of these factors controls the internal force decreases, assigns each factor to the orthogonal table (L ₈ ) by mechanism analysis, and investigates which factor has the effect of reducing the internal force. Went. The results are shown in Table 1.

  The numerical values in Table 1 are the total per one revolution of the internal force applied to the inside of the joint, and when this value increases, the frictional heat increases due to the increase of the internal force and the heat generation amount increases. Here, the value of the spherical clearance Max. Product between the inner ring 20 and the cage 40 was set to 100, and other results were arranged.

  From this analysis result, paying attention to the pocket clearance and the spherical clearance between the inner ring 20 and the cage 40, which are superior in reducing internal force, that is, in the amount of heat generation, the experiment was actually conducted by a two-way analysis with variance. The effects of these factors on fever were investigated. The results are shown in Table 2 and FIGS. 6 and 7.

  From the determination of superiority or superiority in the two-way analysis of variance results, it was found that the pocket clearance and the spherical clearance between the inner ring 20 and the cage 40 have an effect on heat generation. Further, the graphs of FIGS. 6 and 7 show that the pocket clearance is increased and the spherical clearance between the inner ring and the cage 40 is increased in order to reduce the heat generation amount.

  However, by increasing these clearances, the function of the constant velocity universal joint, which is the function of the constant velocity and smooth torque transmission, may be impaired. Therefore, by analyzing the mechanism, the constant velocity universal joint constant velocity and the internal force and clearance sensitivity diagrams (Figs. 8 and 9) were created, and the optimum clearance value was determined. 8 and 9, the sum of internal forces is a value obtained by calculation from mechanism analysis, and it can be estimated that the smaller the value, the smaller the amount of heat generated by friction due to the internal force. In addition, as for the constant velocity, the smaller the value, the better the constant velocity.

  As for the pocket clearance, it is more advantageous to generate heat when the pocket clearance is set larger from the experimental results shown above and the internal force graph (FIG. 8) in the sensitivity diagram. According to the figure, when the pocket clearance is smaller than −0.020 mm, the constant velocity is rapidly deteriorated, and a substantially constant constant velocity can be secured in the region of −0.020 mm to +0.030 mm. However, when the pocket clearance is in the minus side tightness range, a compression force corresponding to the tightness is acting between the ball and the cage from the beginning, and the frictional force between the ball and the cage increases. Therefore, the lower limit of the pocket clearance is set to zero. From the above, the optimum range of the pocket clearance is 0 or more and +0.030 mm or less.

  Regarding the spherical clearance between the inner ring and the cage, the horizontal axis is the clearance ratio in the sensitivity diagram (FIG. 9). This is to express the clearance of large-sized to small-sized constant velocity universal joints on the same scale. As described above, 1000 is obtained by dividing the spherical clearance by the inner spherical reference diameter (= outer ring spherical reference diameter). The multiplied ratio was used as the clearance ratio.

  Looking at the relationship between the clearance ratio and the constant velocity property, the constant velocity property has a good range when the clearance ratio is in the range of 0.60 to 2.60, and the constant velocity property tends to deteriorate outside this range. is there. Since constant velocity is an important function for constant velocity universal joints, the optimum range of the clearance ratio is set to 0.60 as a range in which constant velocity can be secured and the clearance ratio can be increased in consideration of tolerance in mass production. The value is set to 2.60 or less.

From the above, the optimum range of the internal design value for the low heat generation specification of the fixed type constant velocity universal joint is as follows.
Pocket clearance: 0 or more + 0.030mm or less Inner ring to cage spherical clearance ratio: 0.60 or more and 2.60 or less

  A temperature rise comparison confirmation test was performed on the above-mentioned range between a conventional product (comparative example) and an internally designed low heat generation specification product (example), and the results are shown in FIG. As for the test conditions, the fitting angle θ of the joint was fixed at 12 °, and the test was conducted for the rotation speeds of 200 rpm, 600 rpm, and 1000 rpm under the same load torque conditions. The amount of temperature rise is the difference between the temperature of the outer ring surface during operation and the ambient temperature during the test. As is apparent from the figure, the heat generation of the example is about 10 to 20% lower than that of the comparative example.

It is a longitudinal cross-sectional view of the fixed type constant velocity universal joint which shows embodiment of this invention. It is a cross-sectional view of the joint of FIG. It is a principal part enlarged view of FIG. 1 which shows BJ type embodiment. FIG. 3 is an enlarged view of a main part of FIG. 2. It is a principal part enlarged view similar to FIG. 3 which shows UJ type embodiment. It is a diagram which shows the relationship between a pocket clearance and a temperature rise amount. It is a diagram which shows the relationship between the spherical clearance between an inner ring | wheel and a cage, and a temperature rise amount. It is a diagram which shows the relationship between pocket clearance and constant velocity or internal force. It is a diagram which shows the relationship between the spherical clearance ratio between an inner ring | wheel and a cage, and constant velocity or internal force. It is a diagram which shows the relationship between a rotation speed and the temperature rise amount.

Explanation of symbols

10 outer ring 12 inner spherical surface 14 ball groove 16 straight portion 20 inner ring 22 outer spherical surface 24 ball groove 26 straight portion 28 serration or spline 30 ball 40 cage 42 outer spherical surface 44 inner spherical surface 46 pocket

Claims (6)

A plurality of ball grooves extending in the axial direction are formed on the inner spherical surface at equal intervals in the circumferential direction, and an outer ring coupled to the first rotating shaft so as to be able to transmit torque, and a plurality of ball grooves extending in the axial direction are circumferentially formed on the outer spherical surface. An inner ring formed at equal intervals and coupled to the second rotating shaft so as to be able to transmit torque, a plurality of balls that are interposed between the ball groove of the outer ring and the ball groove of the inner ring and transmit the torque, and for accommodating the balls A cage with circumferentially arranged pockets,
The center of the ball groove of the outer joint member is offset from the spherical center of the inner spherical surface, and the center of the ball groove of the inner joint member is offset to the opposite side by an equal distance in the axial direction, respectively. Yes,
A fixed type constant velocity universal joint characterized in that the axial clearance between the pocket and the ball is in the range of 0 to +0.030 mm. A plurality of ball grooves extending in the axial direction are formed on the inner spherical surface at equal intervals in the circumferential direction, and an outer ring coupled to the first rotating shaft so as to be able to transmit torque, and a plurality of ball grooves extending in the axial direction are circumferentially formed on the outer spherical surface. An inner ring formed at equal intervals and coupled to the second rotating shaft so as to be able to transmit torque, a plurality of balls that are interposed between the ball groove of the outer ring and the ball groove of the inner ring and transmit the torque, and for accommodating the balls A cage with circumferentially arranged pockets,
The center of the ball groove of the outer joint member is offset from the spherical center of the inner spherical surface, and the center of the ball groove of the inner joint member is offset to the opposite side by an equal distance in the axial direction, respectively. Yes,
A fixed type constant velocity universal joint characterized in that the clearance ratio of the spherical clearance between the inner ring and the cage is in the range of 0.60 to 2.60. A plurality of ball grooves extending in the axial direction are formed on the inner spherical surface at equal intervals in the circumferential direction, and an outer ring coupled to the first rotating shaft so as to be able to transmit torque, and a plurality of ball grooves extending in the axial direction are circumferentially formed on the outer spherical surface. An inner ring formed at equal intervals and coupled to the second rotating shaft so as to be able to transmit torque, a plurality of balls that are interposed between the ball groove of the outer ring and the ball groove of the inner ring and transmit the torque, and for accommodating the balls A cage with circumferentially arranged pockets,
The center of the ball groove of the outer joint member is offset from the spherical center of the inner spherical surface, and the center of the ball groove of the inner joint member is offset to the opposite side by an equal distance in the axial direction, respectively. Yes,
The axial clearance between the pocket and the ball is in the range of 0 to +0.030 mm, and the clearance ratio of the spherical clearance between the inner ring and the cage is in the range of 0.60 to 2.60. A fixed type constant velocity universal joint.   4. The fixed type constant velocity universal joint according to claim 1, wherein a ball groove of the outer ring and a ball groove of the inner ring have a straight portion in part.   The fixed type constant velocity universal joint according to any one of claims 1 to 4, wherein the fixed type constant velocity universal joint is used for a propeller shaft.   The fixed type constant velocity universal joint according to any one of claims 1 to 5, wherein eight balls are used.

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