JP2007056951A - Nonslip structure for shaft of constant speed joint - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a nonslip structure for a shaft of a constant speed joint which can be easily manufactured in a shaft and an inner part of a joint with both decomposable and undecomposable specifications and can be reduced in the number of man-hours for part control due to shared use of a part to be employed. <P>SOLUTION: The structure includes an inner part of a constant speed joint having an insertion hole 9 for fitting a shaft 6 therewith, the shaft 6 having ring-like stopper ring groove 12, a stopper ring 13 fitted to the stopper ring groove 12 and a ring-like body 17 fitted to the stopper ring groove 12. When a force in a draw-out direction is applied to the shaft 6, an inclined part 16 for applying a force in a diameter contracting direction to the stopper ring 13 is formed in the ring-like body 17 while an inclined part 18 for applying a force in a diameter enlarging direction to the stopper ring 13 is formed in the ring-like body 17. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention is, for example, incorporated in a drive system of an automobile and used for a constant velocity joint that transmits rotational force at a constant speed between rotating shafts that exist on a non-linear line. It is about.

In constant velocity joints incorporated in the drive system of automobiles, etc., a retaining structure has been conventionally used in which the internal parts of the joint and the shaft are removably fitted in order to simplify maintenance work such as boot replacement. . In the structure, a groove is formed at the end of the shaft, and a retaining ring is provided in the groove, and is engaged with a contact surface formed on the joint internal part by elastic expansion of the retaining ring. Then, an angle is provided to the contact surface that interferes with the retaining ring when the shaft is pulled out, and the retaining ring is reduced in diameter by the component force of the interference force with the retaining ring to remove the fitting (patent document) 1, Patent Document 2).
Japanese Patent Laid-Open No. 08-68426 Japanese Utility Model Publication No. 64-5124

  In Patent Document 1, the retaining ring mounting position is on the non-end face side of the shaft, and a tool engaging groove for reducing the diameter of the retaining ring is provided on the end face of the inner ring, so that assembly and disassembly are possible. In this case, time and cost have to be spent on machining the tool engagement groove of the inner ring.

  Further, Patent Document 2 discloses that the retaining ring is reduced in diameter so that it can come out of the shaft. However, how to manage the angle of the inclined portion to establish the specification that comes off and the specification that does not come off. It was not shown what to do.

  In view of the above problems, the present invention can easily produce the shaft and the joint internal parts in both specifications that can be disassembled and specifications that cannot be disassembled, and the parts to be used can be shared. Provided is a structure for preventing a shaft from coming out of a constant velocity joint that can be reduced.

  The structure for preventing the shaft from coming out of the constant velocity joint of the present invention includes a shaft having a ring-shaped retaining ring groove, an internal component of the constant velocity joint having an insertion hole for fitting with the shaft, and the fitting in the retaining ring groove. A retaining ring and a ring-shaped body that fits into the retaining ring groove, and an inclined part that applies a force in the diameter reducing direction to the retaining ring when a pulling direction force is applied to the shaft is formed in the internal part. At the same time, the ring-shaped body is formed with an inclined portion that applies a force in the diameter increasing direction to the retaining ring.

  By changing the angle of the inclined part of the ring-shaped body and the angle of the inclined part of the internal part, the specification that the shaft and the internal part cannot be disassembled or the specification that the shaft and the internal part can be disassembled can be made. . That is, if the inclination angle of the inclined portion that applies the force in the diameter reducing direction to the retaining ring is made a predetermined amount larger than the inclination angle of the inclined portion that applies the force in the diameter increasing direction to the retaining ring, the force in the pulling direction is applied to the shaft. When is added, the force (component force) in the diameter reducing direction acting on the retaining ring is increased, the retaining ring is reduced in diameter, and the shaft can be pulled out from the internal part. If the inclination angle of the inclined portion that applies the force in the diameter reducing direction to the retaining ring is approximately equal to or less than the inclination angle of the inclined portion that applies the force in the diameter expanding direction to the retaining ring, When force is applied, the force in the direction of diameter reduction acts on the retaining ring or does not act, and the shaft cannot be pulled out from the internal part.

  In particular, by changing the angle of the inclined part of the ring-shaped body while keeping the angle of the inclined part of the internal parts fixed, the relationship of the angle of each inclined part can be changed variously. Or a possible specification. That is, when it is desired to make the specification that the shaft and the internal parts cannot be disassembled, by setting 0 ° ≦ (β−α) ≦ 19 °, it becomes difficult to reduce the diameter and it is difficult to disassemble. In addition, when the shaft and the inner ring are to be disassembled, the relationship between the two angles is set to 19 ° <(β−α), so that when the shaft is pulled out, the component force is reduced in the direction of reducing the diameter of the retaining ring. I can pull out the work.

  In the assembled state in which the shaft is fitted in the insertion hole of the internal part, the inclined portion of the ring-shaped body allows the axial and radial component forces to act between the ring-shaped body and the retaining ring. It is possible to eliminate or reduce the axial rattling between the internal parts and the internal parts.

  When the shaft is mounted in the insertion hole of the internal part, the retaining ring groove can be positioned outside the axial range of the spline of the internal part or can be positioned within the axial range.

  In the present invention, by changing the angle of the inclined part of the ring-shaped body and the angle of the inclined part of the internal part, the specification that the shaft and the internal part cannot be disassembled or the shaft and the internal part can be disassembled. Can be. In particular, by changing the angle of the inclined portion of the ring-shaped body while the angle of the inclined portion of the internal part is fixed, it is possible to make the specification incapable of being disassembled or to be able to be disassembled. For this reason, if you prepare multiple types of ring-shaped bodies with inclined parts with different inclination angles without configuring the joint internal parts and shaft as dedicated members, both specifications that can be disassembled and specifications that cannot be disassembled Can be manufactured easily. That is, internal parts and shafts can be shared, and the number of parts management man-hours can be reduced.

  In addition, when the shaft is fitted in the insertion hole of the internal part, the inclined portion of the ring-shaped body can cause the axial and radial component forces to act between the ring-shaped body and the retaining ring. , Axial shakiness between the shaft and internal components can be eliminated or reduced. For this reason, it can be made to function with high precision as a constant velocity joint.

  Hereinafter, the first embodiment of the present invention will be described with reference to FIGS. 1 to 5, and the second embodiment will be described with reference to FIG. 6. When referring to the opposite end side, the right side in the figure is shown. In both the embodiments, a fixed type constant velocity joint as shown in FIG. 1 will be described as an example. In this case, the internal part is an inner ring.

  As shown in FIG. 1, the fixed constant velocity joint 1 includes an outer ring 2, an inner ring 3, a torque transmission ball 4, and a cage 5 for the torque transmission ball 4. A shaft 6 that transmits torque is fitted and attached to the inner ring 3. The constant velocity joint is not limited to the fixed type constant velocity joint 1, but may be a sliding type constant velocity joint such as a double offset type, a cross groove type, or a tripod type. Note that the internal components in the double offset type and the cross groove type are also called inner rings, but in the case of the tripod type, the internal components are called trunnions.

  The outer ring 2 has a large number of curved guide grooves 7 in the axial direction on a spherical inner surface. The inner ring 3 is formed with a large number of curved guide grooves 8 in the axial direction on a spherical outer diameter surface, and an insertion hole 9 for fitting the shaft 6 is formed in the axial direction. A spline 10 is formed on the inner peripheral surface of the insertion hole 9 in the axial direction. An inner ring 3 is provided on the inner surface of the outer ring 2, and a fixed constant velocity joint is formed by positioning a torque transmitting ball 4 via a cage 5 on a ball track formed in cooperation with both guide grooves 7 and 8. is doing.

  An axially extending spline 11 that engages with the spline 10 formed in the insertion hole 9 of the inner ring 3 is formed on the outer periphery of the end portion of the shaft 6, and both the splines are coupled.

  A ring-shaped retaining ring groove 12 is formed on the outer periphery of the spline 11 located on the distal end side of the shaft 6. The position of the retaining ring groove 12 may be within the range of the length of the insertion hole 9 and may be at a position where the spline 11 ends at the tip of the shaft 6.

  As shown in FIG. 2, a ring-shaped retaining ring 13 having a circular cross section is fitted in the retaining ring groove 12. The retaining ring 13 is ring-shaped but partially cut away, and is more outward than the outer diameter of the shaft 6 (the outer diameter including the spline 11) in a state where a force for reducing the diameter is not applied (free state). A part has jumped out. In the state where the diameter has been reduced, the inner surface of the retaining ring groove 12 is entered. For this reason, when the spline 11 of the shaft 6 is engaged with the spline 10 of the inner ring 3, the retaining ring groove 12 is configured so that the retaining ring 13 is reduced in diameter and can pass through the small diameter of the spline 10 of the inner ring 3. Is a depth at which the retaining ring 13 in the reduced diameter state does not interfere.

  In addition, a ring-shaped body 17 having a trapezoidal cross section is fitted into the retaining ring groove 12 on the tip side of the retaining ring 13. The ring-shaped body 17 is also partially cut away, and enters the inner surface side of the retaining ring groove 12 when the diameter is reduced.

  The wall surface on the opposite end side of the ring-shaped body 17 constitutes an inclined portion 18 that is an inclined surface that is sequentially inclined from the outer peripheral side toward the inner peripheral side toward the opposite end side. That is, the shaft 6 is inclined at an angle α with respect to a plane perpendicular to the drawing direction of the shaft 6 (the direction of arrow B in FIG. 2).

  On the distal end side of the insertion hole 9, a large diameter portion 14 having a diameter larger than that of the insertion hole 9 is formed by performing diameter expansion processing. The large diameter portion 14 is continuous via an inclined portion 16 at the end of the spline 10 provided in the insertion hole 9.

  The inclined portion 16 is located on the distal end side outside the axial direction range of the spline 10 and is sequentially inclined from the outer peripheral side toward the inner peripheral side toward the opposite distal end side. In other words, the shaft 6 is inclined at an angle β with respect to a plane perpendicular to the drawing direction of the shaft 6.

  The shaft 6 is attached to the inner ring 3 by placing the retaining ring 13 and the ring-shaped body 17 in the retaining ring groove 12 and reducing the diameter of the retaining ring 13 and the ring-shaped body 17, and then in the direction of arrow A shown in FIG. Then, the shaft 6 is inserted into the insertion hole 9. At this time, the retaining ring 13 and the ring-shaped body 17 are inserted into the spline 10 of the insertion hole 9 while coming into contact (sliding contact) (see FIG. 5). When the tip of the shaft 6 comes out of the insertion hole 9 of the inner ring 3, the end of the inner ring 3 opposite to the tip of the insertion hole 9 and the bulging portion 6a of the shaft 6 (see FIG. 1) come into contact with each other. Thus, further insertion of the shaft 6 is prevented. In order to restrict the insertion allowance of the shaft 6, a retaining ring may be separately attached, and this retaining ring may be in contact with the opposite end side of the insertion hole 9 to prevent further insertion. .

  In the state where the insertion of the shaft 6 into the insertion hole 9 is blocked, as shown in FIG. 2, the retaining ring 13 is positioned at the large diameter portion 14, and the contact with the spline 10 is eliminated. The retaining ring 13 that has been reduced in diameter is expanded by elasticity. When the retaining ring 13 is expanded in diameter, the outer peripheral surface side of the retaining ring 13 is held in contact with the large-diameter portion 14 by an elastic force. Even in this state, the retaining ring 13 is not expanded until it completely comes out of the retaining ring groove 12 and is fitted to the large diameter portion 14, and a part of the retaining ring 13 is still in the retaining ring groove 12. It is in.

  In the state shown in FIG. 2, the ring-shaped body 17 is also slightly expanded in diameter from the reduced diameter, and is in contact with the retaining ring 13 on the outer diameter side of the inclined portion 18. As a result, the inclined portion 18 of the ring-shaped body 17 causes axial and radial component forces to act between the ring-shaped body 17 and the retaining ring 13, and the axial direction between the shaft 6 and the internal components is increased. The rattling can be eliminated or reduced. As shown in FIG. 2, when the shaft 6 is fitted in the insertion hole 9 of the inner ring 3 and no pulling force in the direction of arrow B acts on the shaft 6, The peripheral edge portion should not protrude outward from the outer peripheral surface of the shaft 6.

  Next, the angles α and β of the inclined portions 18 and 16 will be described. The angles α and β are assumed to have the following relationship.

        0 ° <α ≦ β

  The inclined portion 16 defined by the angle β abuts against the opposite end side of the retaining ring 13 when a force in the pulling direction is applied to the shaft, and applies a component force that reduces the diameter of the retaining ring 13.

  In addition, the inclined portion 18 defined by the angle α abuts against the distal end side of the retaining ring 13 when a force in the pulling direction is applied to the shaft, and gives a component force that expands the retaining ring 13.

  If it is assumed that α≈β and the shaft 6 is pulled out along the direction of arrow B in FIG. 2, the inclined portions 18 and 16 with which the retaining ring 13 abuts are substantially parallel to each other, and forces F1 and F2 acting on the retaining ring 13 are obtained. Are less likely to generate a component force that reduces the diameter of the retaining ring 13 due to interference. For this reason, the retaining ring 13 remains fitted to the large-diameter portion 14, and the shaft 6 cannot be pulled out unless the retaining ring 13 is sheared, and the shaft 6 and the inner ring 3 cannot be disassembled. .

  In particular, when the applicant experimented, it was difficult to disassemble the retaining ring 13 without shearing under the condition of 0 ° ≦ (β−α) ≦ 19 °. Therefore, when selecting a specification in which the shaft 6 and the inner ring 3 cannot be disassembled, α and β in this range may be combined.

  Even if a force (component force) acts on the ring-shaped body 17 in the direction of reducing the diameter, the inner peripheral surface 17a of the ring-shaped body 17 has the bottom surface 19 of the retaining ring groove 12 as shown in FIG. The amount of diameter reduction is regulated. In this state, the retaining ring 13 and the inclined portion 18 of the ring-shaped body 17 come into contact with each other, and the extraction of the shaft 6 is restricted.

Further, according to the applicant's experiment, when the inclined portion 18 is 19 ° <(β−α ₁ ) as shown by the two-dot chain line in FIG. 2, the shaft 6 is moved along the arrow B direction in FIG. When pulling out, the forces F3 and F4 acting between the retaining ring 13 and the inclined portions 18 and 16 do not become parallel. For this reason, as a force acting on the retaining ring 13, a component force for reducing the diameter of the retaining ring 13 is generated, and the shaft 6 and the inner ring 3 can be disassembled. Therefore, when selecting a specification for disassembling the shaft 6 and the inner ring 3, α and β in this range may be combined.

  That is, by preparing the inner ring 3 in which the angle of the inclined portion 16 is fixed and a plurality of types of ring-shaped bodies 17 having different angles of the inclined portion 18, the inner ring 3 and the shaft can be combined with the inner ring 3 and the ring-shaped body 17. The specification of what can disassemble 6 and what cannot be disassembled can be selected. Even when the inner ring 3 and the shaft 6 can be disassembled by selecting these angles, it is difficult to disassemble the inner ring 3 and the shaft 6 without using a tool. This is because it is necessary to prevent the shaft 6 from being pulled out during use of the joint even if the specification can be disassembled.

  In this way, by changing the angle of the inclined portion 18 of the ring-shaped body 17 and the angle of the inclined portion 16 of the internal part (inner ring 3), the shaft 6 and the internal part can be made incompatible specifications, The internal parts can be disassembled. In particular, by changing the angle of the inclined portion 18 of the ring-shaped body 17 while the angle of the inclined portion 16 of the internal part is fixed, it is possible to make the specification incapable of being disassembled or to be able to be disassembled. For this reason, if a plurality of types of ring-shaped bodies 17 having inclined portions 18 having different inclination angles are prepared without configuring the internal parts or the shaft 6 as a dedicated member, the specifications can be disassembled and the specifications that cannot be disassembled. Constant velocity joints can be easily manufactured. That is, the internal parts and the shaft 6 can be shared, and the number of parts management man-hours can be reduced.

  In the assembled state in which the shaft 6 is fitted in the insertion hole 9 of the internal part, the axial and radial component forces between the ring-shaped body 17 and the retaining ring 13 are caused by the inclined portion 18 of the ring-shaped body 17. The axial shakiness between the shaft 6 and the internal parts can be eliminated or reduced. For this reason, it can be made to function with high precision as a constant velocity joint.

  Next, a second embodiment will be described with reference to FIGS. 6 and 7. The same components as those in the first embodiment are denoted by the same reference numerals, and detailed description thereof will be omitted. 2nd Embodiment shows the example which provided the inclination part 20 with the retaining ring 13 in the middle of the spline 10 of the inner ring | wheel 3. As shown in FIG. That is, in the first embodiment, when the shaft 6 is mounted in the insertion hole 9 of the inner ring 3, the retaining ring groove 12 is positioned outside the axial range of the spline 10 of the inner ring 3, whereas the second In this embodiment, the retaining ring groove 12 is positioned within the axial range of the spline 10 of the inner ring 3. In the second embodiment as well, for convenience of explanation, the left side in the figure is shown for the tip side, and the right side in the figure is shown for the anti-tip side.

  A circumferential groove 21 is formed in the middle of the front end side of the spline 10 of the insertion hole 9 formed in the inner ring 3. The depth of the groove 21 is slightly deeper than the height of the spline 10. The groove 21 is formed in a size that can receive the retaining ring 13, and the opening and groove of the retaining ring groove 12 described above in a state where the shaft 6 is fitted (attached) to the insertion hole 9 of the inner ring 3. 21 opening is opposed.

  The wall on the opposite end side of the groove 21 is an inclined surface that inclines toward the opposite end side from the outer diameter side toward the inner diameter side. This inclined wall becomes an inclined portion 20 that applies a force in the diameter reducing direction to the retaining ring 13 when a force in the pulling direction of the shaft 6 is applied. The inclination angle of the inclined portion 20 is defined as an angle β with reference to a plane perpendicular to the drawing direction of the shaft 6.

  Also in this case, the shaft 6 is attached to the inner ring 3 by disposing the retaining ring 13 and the ring-shaped body 17 in the retaining ring groove 12 and reducing the diameter of the retaining ring 13 and the ring-shaped body 17, and then removing the shaft 6. It inserts in the insertion hole 9 along the arrow A direction shown in FIG. At this time, the retaining ring 13 and the ring-shaped body 17 are inserted into the spline 10 of the insertion hole 9 while coming into contact (sliding contact).

  In the state where the insertion of the shaft 6 into the insertion hole 9 is blocked (the state where the shaft 6 is fitted in the insertion hole 9), the retaining ring 13 and the ring-shaped body 17 that have been reduced in diameter are connected to the inner diameter of the spline 10. Since there is no contact, the diameter is expanded by elasticity. When the diameter of the retaining ring 13 is increased, the outer peripheral surface side of the retaining ring 13 is fitted in the groove 21 as shown in FIG.

  In the state shown in FIG. 6, the diameter of the ring-shaped body 17 is also slightly increased from the reduced state, and the retaining ring 13 contacts the outer diameter side of the inclined portion 18. For this reason, also in the second embodiment, the inclined portion 18 of the ring-shaped body 17 causes axial and radial component forces to act between the ring-shaped body 17 and the retaining ring 13, and the shaft It is possible to eliminate or reduce axial rattling between 6 and the internal parts. In the state where the pulling force in the direction of arrow B is not acting on the shaft 6, the outer peripheral edge portion of the ring-shaped body 17 is prevented from protruding beyond the outer peripheral surface of the shaft 6.

  The angles α and β of the inclined portions 18 and 20 are as shown in FIG. 6 under the condition of α≈β or 0 ° ≦ (β−α) ≦ 19 ° under the same conditions as in the first embodiment. As described above, the forces F5 and F6 (see FIG. 7) acting on the retaining ring 13 interfere with each other, and the retaining ring 13 remains fitted in the groove 21. For this reason, unless the retaining ring 13 is sheared, the shaft 6 cannot be pulled out, and the shaft 6 and the inner ring 3 cannot be disassembled.

In addition, as shown by the two-dot chain line in FIG. 6, in the condition that 19 ° <(β−α ₁ ), the inclined portion 18 is stopped as forces F7 and F8 (see FIG. 6) acting on the retaining ring 13. Since the component force which moves the ring | wheel 13 to a diameter reduction direction (center-axis direction of a shaft) arises, the shaft 6 and the inner ring | wheel 3 can be disassembled.

  That is, even in the second embodiment, the same operational effects as those in the first embodiment can be obtained.

  In each of the above embodiments, the retaining ring 13 has a circular cross section, but the cross section may be a rectangle or an ellipse, and the ring-shaped body 17 is not limited to a trapezoidal section. When the force in the pulling direction is applied to the retaining ring 13, the inclined portion 18 that applies the force in the diameter expanding direction to the retaining ring 13 may be provided.

  When setting the inclination angles of the inclined portions 16, 18, and 20, it is preferable that the angle of the inclined portion 16 of the internal component is fixed (constant) so that it can be disassembled or cannot be disassembled. It is not necessary to fix the angles of the inclined parts 16 and 20 of the parts.

It is sectional drawing of the constant velocity joint which shows the 1st Embodiment of this invention. It is a principal part expanded sectional view of the said constant velocity joint. It is an expanded sectional view when extraction force acts on a shaft. It is sectional drawing which shows the state before an assembly of a shaft and an inner ring. It is an expanded sectional view in the middle of assembly of a shaft and an inner ring. It is principal part sectional drawing of the constant velocity joint which shows the 2nd Embodiment of this invention. It is sectional drawing which shows the state before the assembly of the shaft and inner ring | wheel of the said constant velocity joint.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Fixed type constant velocity joint 2 Outer ring 3 Inner ring 4 Ball for torque transmission 5 Cage 6 Shaft 6a Expansion part 7, 8 Guide groove 9 Insertion hole 10, 11 Spline 12 Retaining ring groove 13 Retaining ring 14 Large diameter part 16, 18 , 20 Inclined portion 17 Ring-shaped body 17a Inner peripheral surface 19 Bottom surface 21 Groove

Claims (5)

A shaft having a ring-shaped retaining ring groove;
An internal component of a constant velocity joint having an insertion hole for fitting with a shaft;
A retaining ring that fits into the retaining ring groove;
A ring-shaped body that fits into the retaining ring groove,
When the pulling direction force is applied to the shaft, an inclined portion that applies a force in the diameter reducing direction to the retaining ring is formed in the internal part, and the inclined portion that applies a force in the diameter increasing direction to the retaining ring is formed in the ring-shaped body. A structure for preventing the shaft from coming out of the constant velocity joint.   The inclination angle of the inclined portion is based on a plane perpendicular to the drawing direction of the shaft, the angle of the inclined portion of the ring-shaped body is α, the angle of the inclined portion of the internal part is β, and the relationship between the two angles The structure for preventing the shaft from coming out of the constant velocity joint according to claim 1, wherein the shaft and the internal parts cannot be disassembled by satisfying 0 ° ≦ (β−α) ≦ 19 °.   The inclination angle of the inclined portion is based on a plane perpendicular to the drawing direction of the shaft, the angle of the inclined portion of the ring-shaped body is α, the angle of the inclined portion of the internal part is β, and the relationship between the two angles The structure for preventing the shaft from coming out of the constant velocity joint according to claim 1, wherein the shaft and the internal parts can be disassembled by satisfying 19 ° <(β−α).   The shaft and the internal part are coupled by a spline, and when the shaft is installed in the insertion hole of the internal part, the retaining ring groove is located outside the axial range of the spline of the internal part. Item 4. The structure for preventing shaft dropout of the constant velocity joint according to any one of Items 1 to 3.   The shaft and the internal part are coupled by a spline, and when the shaft is mounted in the insertion hole of the internal part, the retaining ring groove is located within the axial range of the spline of the internal part. Item 4. The structure for preventing shaft dropout of the constant velocity joint according to any one of Items 1 to 3.