JP2007255464A - Constant velocity universal joint - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a constant velocity universal joint capable of preventing excessive increase of slide resistance and improving workability of work for mounting it on a vehicle, durability, and vehicle vibration characteristic. <P>SOLUTION: This constant velocity universal joint is constituted by incorporating balls 23 in a crossing part of a track groove 26 of an inner ring 21 and a track groove 27 of an outer ring 22 and holding these balls 23 by a cage 24. Projecting parts 40, 55 protruding on an inside diameter side are provided in cylindrical parts 37a, 53a of an end plate 37 and a boot adapter 53, and recessed parts 41, 56 are provided in cut-out parts 42, 57 on an outer peripheral face of the outer ring 22. While the cylindrical parts 37a, 53a are externally fitted into the outer ring 22 and the end plate 37 and the boot adapter 53 are fixed to the outer ring 22 by tightening them by a tightening bolt 36, clearances 45, 65 are formed among inner peripheral faces 43, 58 of the cylindrical parts 37a, 53a, the cut-out parts 42, 57 on the outer peripheral face, and cut-out peripheral faces 44, 64, and the projecting parts 40, 55 are fitted into the recessed parts 41, 56. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention is a power transmission device used for automobiles, various industrial machines, and the like, and is particularly incorporated in a propeller shaft or the like used in 4WD vehicles, FR vehicles, etc., and has a structure capable of absorbing axial displacement, etc. It relates to a universal joint.

  Propeller shafts used in automobiles such as 4WD vehicles and FR vehicles include a constant velocity universal joint so as to be able to cope with axial displacement and angular displacement due to a relative position change between the transmission and the differential. Usually, from the viewpoint of reducing the weight of the entire vehicle, a sliding type constant velocity universal joint called a Lebro type (or a cross groove type) that is lightweight and has good rotational balance and vibration characteristics is incorporated.

  The Lebro type constant velocity universal joint is roughly classified into two types, a float type and a non-float type, and both types are properly used according to the characteristics (slide amount, etc.) of the vehicle equipped with the propeller shaft.

  As shown in FIG. 11, both types of constant velocity universal joints have an inner ring 1, an outer ring 2, a ball 3 and a cage 4 as main components. FIG. 11 shows a float type.

  The inner ring 1 has a plurality of track grooves 6 formed on the outer peripheral surface thereof. A stub shaft 8 of a propeller shaft is inserted into the center hole 5 of the inner ring 1 and is spline-fitted, and torque can be transmitted between the two by the spline fitting. The stub shaft 8 is prevented from coming off from the inner ring 1 by a snap ring 11.

  The outer ring 2 is located on the outer periphery of the inner ring 1, and the same number of track grooves 7 as the track grooves 6 of the inner ring 1 are formed on the inner peripheral surface thereof. The track groove 6 of the inner ring 1 and the track groove 7 of the outer ring 2 form an angle inclined in opposite directions with respect to the axis, and the ball 3 is formed at the intersection of the track groove 6 of the inner ring 1 and the track groove 7 of the outer ring 2 that make a pair. Is incorporated. A cage 4 is disposed between the inner ring 1 and the outer ring 2, and the ball 3 is held in a pocket 9 of the cage 4.

  The outer ring 2 is attached to a vehicle mounting flange (companion flange) (not shown). In other words, the end plate 10 (cap for preventing leakage of grease filled in the joint and preventing entry of foreign matter) is sandwiched between the vehicle mounting flange and the outer ring 2 and inserted into the insertion hole 17 of the outer ring 2. A bolt member (not shown) is screwed into the screw hole of the vehicle mounting flange. Thus, the constant velocity universal joint is fastened to the vehicle mounting flange.

  The end plate 10 includes a cylindrical portion 10a, a deep dish-shaped portion 10b that bulges toward the outer ring side, and a ring-shaped flat plate portion 10c that connects the cylindrical portion 10a and the deep dish-shaped portion 10b. The tubular portion 10 a is fitted on the outer ring end portion on the flange side of the outer peripheral surface 16. That is, as shown in FIG. 12, a notch portion 20 is provided at the end of the outer ring, and a cylindrical portion 10 a is externally fitted to the notch portion 20. In addition, as shown in FIG. 1, the ring-shaped flat plate portion 10c is provided with a through hole 18 through which the bolt member is inserted.

  A sealing device 15 is mounted on the opposite side of the outer ring 2 from the flange side. The sealing device 15 includes a boot 12 and a metal boot adapter 13 in order to suppress the rotational expansion of the boot during high-speed rotation. The boot 12 has a small end portion and a large end portion, and is shaped to be folded back into a V shape in the middle. The boot adapter 13 includes a large-diameter cylindrical portion 13a, a small-diameter cylindrical portion 13b, and a ring-shaped flat plate portion 13c that connects the cylindrical portions 13a and 13b. The cylindrical portion 13a is an anti-flange of the outer peripheral surface 16. It is fitted on the outer ring end on the side. The ring-shaped flat plate portion 13 c is provided with a through hole 19 through which the bolt member is inserted.

  Accordingly, the end plate 10 and the boot adapter 13 are fixed to the outer ring 2 by bolting with the bolt member, and the outer ring 2 to which the end plate 10 and the boot adapter 13 are attached is attached to the vehicle mounting flange. At this time, the ring-shaped flat plate portion 10 c of the end plate 10 is in pressure contact with the end surface 2 a on the flange side of the outer ring 2, and the ring-shaped flat plate portion 13 c of the boot adapter 13 is in pressure contact with the end surface 2 b on the opposite side of the outer ring 2. A small end portion of the boot 12 is attached to the stub shaft 8 and fastened by a boot band 14, and a large end portion of the boot 12 is held by crimping an end portion of the boot adapter 13.

  In the Lebro type constant velocity universal joint configured as described above, the outer ring track and the inner ring track cross each other, so that the joint internal clearance (PCD clearance) can be set by tightening. For this reason, the circumferential direction inside the joint can be eliminated, and it is suitable for a propeller shaft that rotates at high speed.

  Such a constant velocity universal joint is assembled at a factory other than an automobile manufacturer, for example, and is transported to an automobile manufacturer or the like in the state shown in FIG. 11 and incorporated into a vehicle by the automobile manufacturer or the like. For this reason, it is mounted on a vehicle mounting flange (companion flange) via a bolt member inserted into the insertion hole 17 of the outer ring 2. For this reason, conventionally, the end plate 10 and the boot adapter 13 have been press-fitted into the outer ring 2 so that the end plate 10 and the boot adapter 13 do not come off during transportation.

  However, when the end plate 10 and the boot adapter 13 are attached by press fitting, the joint internal clearance is set as a tightening allowance, and the tightening allowance is further tightened inside the joint by these attachments (press fit). That is, since the end plate 10 and the boot adapter 13 are press-processed products, the manufacturing tolerance of the inner diameter is larger than that of the machined product, and the tightening allowance with the outer ring 2 is also increased.

  For this reason, the resistance value as a joint assembly increases by press fitting assembly of boots, end plates, etc. with respect to the initial setting of the slide resistance value of the joint alone (state before assembly of boots, end plates, shafts, etc.). It will be.

  An increase in slide resistance (excessive) leads to a decrease in propeller shaft mounting workability, a decrease in service life due to increased heat generation in the joint, generation of vehicle vibration, and the like.

  Therefore, as a method of attaching the end plate to the outer ring, there is a method in which the end plate is not externally fitted to the outer ring (Patent Document 1 and Patent Document 2). The thing of patent document 1 is providing the counterbore part in the outer end surface of an outer ring | wheel, and has provided the 1st nail | claw and the 2nd nail | claw in the outer edge part of the end plate. That is, the inner peripheral surface of the spot facing portion is a tapered surface whose diameter increases from the opening toward the bottom, and the first pawl of the end plate is in elastic contact with the tapered surface, and the bottom end of the spot facing portion ends. The second claw of the plate is in contact.

Also, the one described in Patent Document 2 is provided with a counterbore portion on the outer end surface of the outer ring, and the circular flat plate portion of the end plate is fitted to the counterbore portion via a buffer member in the same manner as that described in Patent Document 1. I am letting.
Japanese Utility Model Publication No. 5-79056 German Patent DE 197353646A1

  In the thing of the said patent document 1, in the state before fastening a fastening bolt, what was called temporarily fixed to the outer ring | wheel by making the 1st nail | claw of an end plate elastically contact | abut to the taper surface of a counterbore part. In this state, it is transported to the vehicle assembly location. However, in such a temporarily fixed state, the holding force of the end plate is small, and there is a possibility that the end plate is detached from the outer ring during handling such as transportation.

  Moreover, in the thing of patent document 2, in the state before tightening the fastening bolt, the end plate is in a state that is not temporarily fixed to the outer ring. For this reason, when conveying to a vehicle assembly place, it is necessary to convey an end plate as another member, and the handleability is inferior.

  In view of the above problems, the present invention provides a constant velocity universal joint that can eliminate excessive slide resistance and can improve vehicle installation workability, durability, and vehicle vibration characteristics.

  In the constant velocity universal joint of the present invention, linear track grooves are formed in each of the outer peripheral surface of the inner ring and the inner peripheral surface of the outer ring in the axial direction in a state where they are inclined in directions opposite to each other in the axial direction. A cylinder that incorporates balls in the intersection of the grooves, holds the balls by a cage disposed between the outer peripheral surface of the inner ring and the inner peripheral surface of the outer ring, and is fitted to the end of the outer ring on the vehicle mounting flange side. In the constant velocity universal joint having an end plate having a portion and a sealing device for closing the outer ring opening at the outer ring end on the opposite flange side, the sealing device is externally fitted on the outer ring end on the opposite flange side. A metal boot adapter having a cylindrical portion, a shaft connected to an inner ring, and a boot attached to the boot adapter. The cylindrical portion of the end plate and the boot adapter has a protruding portion protruding toward the inner diameter side. The outer ring is provided with a recess in the outer ring, the cylindrical portion is fitted onto the outer ring, and the end plate and the boot adapter are axially pressed against the outer ring by tightening with a tightening bolt. Thus, a gap is formed between the inner peripheral surface of the cylindrical portion and the outer peripheral surface of the outer ring, and the protruding portion is fitted into the recess.

  In the constant velocity universal joint of the present invention, the projections of the end plate and the boot adapter are fitted in the recesses provided in the outer ring, so that the end plate and the boot adapter are not yet tightened with a tightening bolt or the like. Even in this case, the end plate and the boot adapter can be held on the outer ring.

  Further, since a gap is formed between the inner peripheral surface of the cylindrical portion and the outer peripheral surface of the outer ring in a state where the cylindrical portion is fixed to the outer ring, in this external fitting fixed state, the tightening force in the inner diameter direction with respect to the outer ring is reduced. It's small. And since a sealing device consists of a metal boot adapter and a boot, the rotation expansion of the boot at the time of high speed rotation can be suppressed.

  In a state where the end plate and the boot adapter are fixed to the outer ring, a space is formed on the axially outward side of the opening end of the cylindrical portion. Thereby, the fastening force by the fastening bolt can be stably applied without deforming the end plate and the boot adapter.

  The protrusions may be formed by small convex ridges that are arranged at a predetermined pitch along the circumferential direction on the inner peripheral surface of the cylindrical part. Further, the protruding portion may be provided at the axially central portion of the cylindrical portion. Furthermore, even if the said projection part was provided in the axial direction edge part of a cylinder part, the axial direction edge part of a cylinder part may be return | folded to the internal-diameter side, and the projection part may be comprised. Moreover, even if the cross-sectional shape of a projection part is the shape of the cross section V, the convex curve shape which bulges to an internal diameter side may be sufficient.

  According to the constant velocity universal joint of the present invention, the end plate and the boot adapter can be held on the outer ring even before the end plate and the boot adapter are tightened with a tightening bolt or the like. For this reason, when the vehicle is assembled (attached), the end plate and the boot adapter are attached to the outer ring, so that the handleability is improved.

  In addition, in the state where the cylindrical portion having the protruding portion is fitted and fixed to the outer ring, a gap is formed between the inner peripheral surface of the cylindrical portion and the outer peripheral surface of the outer ring without the protruding portion. In the fitted and fixed state, the tightening force in the inner diameter direction with respect to the outer ring may be small. For this reason, it is possible to prevent the slide resistance from being excessively increased, and it is possible to improve vehicle installation workability, durability, and vehicle vibration characteristics.

  With the end plate and boot adapter fixed to the outer ring, a space is formed on the axially outward side of the open end of the cylinder, so the tightening force by the tightening bolt can be used to deform the end plate and boot adapter, etc. It can be stably applied without causing it. As a result, the end plate and the boot adapter can be securely fixed to the outer ring, and the PCD clearance is not affected.

  An embodiment of a constant velocity universal joint according to the present invention will be described with reference to FIGS.

  As an embodiment of the present invention, FIGS. 1 and 2 show a float type Lebro type (or cross groove type) constant velocity universal joint in which the minimum inner diameter of the cage is set larger than the maximum outer diameter of the inner ring. It can be applied to a non-float type.

  The constant velocity universal joint in this embodiment includes an inner ring 21, an outer ring 22, a ball 23, and a cage 24 as main components.

  The inner ring 21 has a plurality of track grooves 26 formed on the outer peripheral surface thereof. A stub shaft 28 is inserted into the center hole 25 of the inner ring 21 and is spline-fitted, and the torque can be transmitted between the two by the spline fitting. The stub shaft 28 is prevented from coming off from the inner ring 21 by a snap ring 31.

  The outer ring 22 is located on the outer periphery of the inner ring 21, and the same number of track grooves 27 as the track grooves 26 of the inner ring 21 are formed on the inner peripheral surface thereof. As shown in FIG. 2, the track groove 26 of the inner ring 21 and the track groove 27 of the outer ring 22 form an angle inclined in the opposite direction to the axis (track crossing angle α), and the track groove 26 of the inner ring 21 that forms a pair. A ball 23 is incorporated at the intersection of the outer ring 22 and the track groove 27. A cage 24 is disposed between the inner ring 21 and the outer ring 22, and the ball 23 is held in a pocket 29 of the cage 24.

  The outer ring 22 is attached to a vehicle mounting flange (companion flange) 34 having a hollow portion 33. That is, the outer ring 22 is provided with axial insertion holes 35 arranged at a predetermined pitch along the circumferential direction, and a bolt member (clamping bolt) 36 inserted through the insertion hole 35 is used as a vehicle mounting flange. 34 are screwed into the screw holes 30. As a result, the constant velocity universal joint can be fastened to the vehicle mounting flange 34.

  A sealing device 50 is mounted on the opposite side of the outer ring 22 from the flange. The sealing device 50 includes a boot 52 and a metal boot adapter 53 in order to suppress the rotational expansion of the boot during high-speed rotation. The boot 52 has a small end portion 52b and a large end portion 52a, and is shaped like a V-shape in the middle. The boot adapter 53 includes a large-diameter cylindrical portion 53a, a small-diameter cylindrical portion 53b, and a ring-shaped flat plate 53c that connects the cylindrical portion 53a and the cylindrical portion 53b. A small end 52 b of the boot 52 is attached to the stub shaft 28 and fastened with a boot band 54. The large end 52 a of the boot 52 is held by crimping the end of the boot adapter 53.

  An end plate 37 is attached to the outer ring end on the vehicle mounting flange side. The end plate 37 closes the joint opening on the side of the vehicle mounting flange, and prevents leakage of grease filled in the joint and prevents foreign substances from entering. The end plate 37 connects the cylindrical portion 37a that is externally fitted to the outer ring end on the vehicle mounting flange side, the deep dish-shaped portion 37b that bulges toward the opposite outer ring, and the cylindrical portion 37a and the deep-plate shaped portion 37b. And a ring-shaped flat plate portion 37c.

  As shown in FIG. 3, the cylindrical portion 37 a of the end plate 37 is provided with a protruding portion 40 including a ring-shaped bulging portion protruding toward the inner diameter side, and the protruding portion 40 is formed on the notched portion 42 of the outer peripheral surface 38 of the outer ring 22. A recess 41 into which the portion 40 is fitted is provided. That is, the projecting portion 40 has a convex curved shape whose cross-sectional shape bulges toward the inner diameter side, and a notch 42 is formed along the circumferential direction at one end 38 a of the outer peripheral surface 38 of the outer ring 22. A recess 41 is formed in the portion 42. The curvature radius of the protrusion 40 is set smaller than the curvature radius of the recess 41. For this reason, in a state where the protrusion 40 is fitted in the recess 41, gaps 48 and 49 are formed on both axial sides of the protrusion 40.

  Further, through-holes 47 are provided at a predetermined pitch along the circumferential direction in the ring-shaped flat plate portion 37c of the end plate 37. By inserting the tightening bolts 36 into the through-holes 47, the end plate 37 is The ring-shaped flat plate portion 37 c abuts on the outer ring end surface 22 a on the flange side of the outer ring 22, and is held between the outer ring 22 and the flange 34. In the state where the end plate 37 is attached to the outer ring 22, the inner circumferential surface 43 of the cylindrical portion 37 a is not in contact with the outer circumferential surface cutout portion 42 and the cutout circumferential surface 44 of the outer ring 22, and the gap 45 is formed. In this state, the protrusion 40 is fitted into the recess 41.

  That is, as shown in FIG. 4, the diameter dimension (end plate mounting portion outer diameter) of the notch 42 of the outer ring 22 is D1, the bottom diameter of the recess 41 (minimum recess diameter) is D2, and the end plate 37 When the inner diameter of the cylindrical portion 37a is d1, and the inner diameter of the protrusion 40 is d2, the relationship of D1 <d1 and the relationship of d2 <D1 are established.

  At this time, it is preferable to set d2 slightly smaller than D2. As a result, the protrusion 40 comes into pressure contact with the bottom of the recess 41. That is, the protrusion 40 is press-fitted into the recess 41. In such press-fitting, the tightening force in the inner diameter direction is small, and there is almost no influence on the inside of the joint. Further, d2 and D2 may be the same, and the protrusion 40 may be in contact (contact) with the bottom of the recess 41.

  As shown in FIG. 3, the axial length L of the notch 42 is longer than the axial length L <b> 1 of the cylindrical portion 37 a of the end plate 37. For this reason, by tightening the fastening bolt 36, a space S is formed on the axially outward side of the cylindrical portion 37a at the opening end of the cylindrical portion 37a when the end plate 37 is mounted on the outer ring 22.

  As shown in FIG. 5, the cylindrical portion 53 a of the boot adapter 53 of the sealing device 50 is provided with a protruding portion 55 that protrudes toward the inner diameter side, and the protruding portion 55 is formed in the notched portion 57 of the outer peripheral surface 38 of the outer ring 22. A recess 56 is provided in which is fitted. That is, the protrusion 55 has a cross-sectional shape similar to that of the protrusion 40 shown in FIG. 3, and a notch 57 is formed in the other end 38b of the outer peripheral surface 38 of the outer ring 22 along the circumferential direction. A recess 56 is formed in the portion 57. The radius of curvature of the projection 55 is set to be smaller than the radius of curvature of the recess 56, and gaps 62 and 63 are formed on both sides in the axial direction of the projection 55.

  Further, through holes 61 are provided at a predetermined pitch along the circumferential direction in the ring-shaped flat body 53 c of the boot adapter 53, and the boot bolt 53 is inserted into the through holes 61 so that the boot adapter 53 is attached to the outer ring 22. Can be installed on. That is, the end plate 37 and the boot adapter 53 can be attached to the outer ring 22 by screwing the fastening bolt 36 into the screw hole 30 of the flange 34, and the outer ring on which the end plate 37 and the boot adapter 53 are mounted. 22 can be attached to the flange. The end plate 37 and the boot adapter can be sealed with packing or the like, and there is no fear of grease leakage.

  Also in this case, the boot adapter 53 and the outer ring 22 have the same relationship as the relationship between the end plate 37 and the outer ring 22. That is, the diameter dimension (outer diameter of the adapter mounting portion) of the notch 57 of the outer ring 22 is D1, the bottom diameter of the recess 56 (minimum diameter of the recess) is D2, and the inner diameter of the cylindrical portion 53a of the boot adapter 53 is d1. When the inner diameter of the protrusion 55 is d2, the relationship of D1 <d1 and the relationship of d2 <D1 are established. As a result, the inner peripheral surface 58 of the cylindrical portion 53a is not in contact with the outer peripheral surface cutout portion 57 and the cutout peripheral surface 64 of the outer ring 22, and a gap 65 is formed. In this state, the protrusion 55 is fitted in the recess 56.

  Even in this case, it is preferable to set d2 slightly smaller than D2. As a result, the protrusion 55 is pressed against the bottom of the recess 56. That is, the protrusion 55 is press-fitted into the recess 56. Note that such press fitting hardly affects the inside of the joint. Further, d2 and D2 may be the same, and the protrusion 55 may be in contact (contact) with the bottom of the recess 56.

  The axial length L of the notch 57 is also longer than the axial length L1 of the tubular portion 53a of the boot adapter 53. Thus, by tightening the tightening bolt 36, the protrusion 55 can be fitted in the recess 56 in a state where the ring-shaped flat plate 53 c is in contact with the outer ring end surface 22 b on the side opposite to the flange of the outer ring 22. . In addition, in this state, a space S is formed on the axially outer side of the opening end of the cylindrical portion 53a.

  According to the present invention, the end plate 37 and the boot adapter 53 can be held by the outer ring even before the end plate 37 and the boot adapter 53 are tightened by the tightening bolts 36. For this reason, when the vehicle is assembled (attached), the end plate and the boot adapter are attached to the outer ring, so that the handleability is improved.

  Further, in a state where the cylindrical portions 37a and 53a having the protruding portions 40 and 55 are fitted and fixed to the outer ring, the inner peripheral surfaces 43 and 58 of the cylindrical portions 37a and 53a are omitted from the outer ring 22 by omitting the protruding portions 40 and 55. Since the gaps 45 and 65 are formed between the outer peripheral surface cutout portions 42 and 57 and the cutout peripheral surfaces 44 and 64, in this external fitting fixed state, the tightening force in the inner diameter direction with respect to the outer ring may be small. For this reason, it is possible to prevent the slide resistance from being excessively increased, and it is possible to improve vehicle installation workability, durability, and vehicle vibration characteristics.

  In a state where the end plate 37 and the boot adapter 53 are fixed to the outer ring 22, a space S is formed on the axially outward side of the open ends of the cylindrical portions 37a and 53a. As a result, the tightening force by the tightening bolt 36 can be stably applied without deforming the end plate 37 and the boot adapter 53. The end plate 37 and the boot adapter 53 can be securely fixed to the outer ring 22, and the joint internal clearance (PCD clearance) is not affected.

  By the way, as the protrusion part 40 of the end plate 37, as shown in FIG. 6, the cross-sectional shape may be V-shaped. Further, as shown in FIGS. 7 and 8, the protrusion 40 may be provided at the axial end of the cylindrical portion 37a. The protrusion 40 has an arc shape in cross section in FIG. 7 and a V shape in cross section in FIG. Moreover, as shown in FIG. 9, the protrusion part 40 can also be comprised by forming the internal diameter direction bending part 66 in the axial direction edge part of the cylinder part 37a.

  Even in the case shown in FIGS. 6 to 9, the end plate 37 is pressed against the outer ring 22 in the axial direction by tightening with the tightening bolt 36, and the inner peripheral surface 43 of the cylindrical portion 37a is fixed. A gap 45 is formed between the outer circumferential surface cutout portion 42 and the cutout circumferential surface 44 of the outer ring 22, and the protrusion 40 is fitted into the recess 41. Further, with the end plate 37 fixed to the outer ring 22, a space S is formed on the axially outer side of the open end of the cylindrical portion 37a. For this reason, it is what is shown in FIGS. 6-9, Comprising: The effect similar to what is shown in FIG. 3 etc. can be show | played.

  Moreover, in the said embodiment, although the projection part 40 continued in the circumferential direction, as shown in FIG. 10, the projection part 40 is a predetermined pitch along the circumferential direction on the internal peripheral surface 43 of the cylinder part 37a. Small convex ridges in which a plurality are provided may be used.

  6 to 10 show the relationship between the end plate 37 and the outer ring 22, the projection 40 and the recess 41 are formed in the cylindrical portion 53 a of the boot adapter 53 and the outer peripheral surface notch 57 of the outer ring 22. It may be provided.

  As described above, the embodiment of the present invention has been described. However, the present invention is not limited to the above-described embodiment, and various modifications are possible. For example, the inner peripheral surfaces 43 and 58 of the cylindrical portions 37a and 53a and the outer ring 22 are possible. The size of the gaps 45 and 65 between the outer peripheral surface cutout portions 42 and 57 and the cutout peripheral surfaces 44 and 64 can be arbitrarily set, but is preferably set to 0.3 mm or less, for example. . If it exceeds this, the outer diameter of the cylinder portion will increase, and the attachment to the flange 34 and the like will be inferior. Further, the space S formed on the axially outer side of the opening ends of the cylindrical portions 37a and 53a may be omitted. At this time, it is preferable that when the tightening bolts 36 are tightened, the opening ends of the cylindrical portions 37a and 53a abut on the notched inner ends of the notched portions 42 and 57.

It is sectional drawing of the constant velocity universal joint which shows embodiment of this invention. It is a partial front view for demonstrating the track crossing angle in the inner ring | wheel and outer ring | wheel of the said constant velocity universal joint. It is principal part sectional drawing of the mounting state of the end plate of the said constant velocity universal joint. It is a disassembled sectional view of the outer ring and end plate of the constant velocity universal joint. It is principal part sectional drawing of the mounting state of the boot adapter of the said constant velocity universal joint. It is principal part sectional drawing of the 1st modification of an end plate. It is principal part sectional drawing of the 2nd modification of an end plate. It is principal part sectional drawing of the 3rd modification of an end plate. It is principal part sectional drawing of the 4th modification of an end plate. It is a principal part simplification figure of the 5th modification of an end plate. It is sectional drawing of the conventional constant velocity universal joint. It is a principal part expanded sectional view of the conventional constant velocity universal joint.

Explanation of symbols

21 Inner ring 22 Outer ring 23 Ball 24 Cage 26, 27 Track groove 34 Flange 36 Tightening bolt 37 End plate 37a Tube portion 38 Outer peripheral surface 53a Tube portion 40, 55 Projection portion 41, 56 Recess portion 42, 57 Notch portion 43, 58 Inside Peripheral surfaces 44, 64 Notched peripheral surfaces 45, 65 Clearance 50 Sealing device 52 Boot 53 Boot adapter 66 Inner diameter direction bent portion S Space

Claims (9)

A straight track groove is formed on each of the outer peripheral surface of the inner ring and the inner peripheral surface of the outer ring in the axial direction in a state of being inclined in opposite directions with respect to the axial direction, and balls are incorporated at the intersections of both track grooves, The ball is held by a cage disposed between the outer peripheral surface of the inner ring and the inner peripheral surface of the outer ring, and an end plate having a cylinder portion fitted on the outer ring end portion on the vehicle mounting flange side is mounted. In the constant velocity universal joint equipped with a sealing device for closing the outer ring opening at the outer ring end on the opposite flange side,
The sealing device includes a metal boot adapter having a cylindrical portion fitted on the outer ring end portion on the opposite flange side, a shaft connected to an inner ring, and a boot attached to the boot adapter, and an end plate In addition, the cylindrical portion of the boot adapter is provided with a protruding portion that protrudes toward the inner diameter side, and a recess is provided in the outer peripheral surface of the outer ring. The cylindrical portion is fitted on the outer ring, and is tightened with a tightening bolt to end plate In the fixed state where the boot adapter is pressed in the axial direction against the outer ring, a gap is formed between the inner peripheral surface of the cylindrical portion and the outer peripheral surface of the outer ring, and the protrusion is fitted in the recess. A constant velocity universal joint characterized by   2. The constant velocity universal joint according to claim 1, wherein a space is formed on the axially outward side of the opening end of the cylindrical portion in a state where the end plate and the boot adapter are fixed to the outer ring.   The constant velocity universal joint according to claim 1 or 2, wherein the protrusion is a ring-shaped bulging portion disposed on the entire inner peripheral surface of the cylindrical portion.   3. The constant velocity universal joint according to claim 1, wherein the protrusions are small convex ridges arranged at a predetermined pitch along the circumferential direction on the inner peripheral surface of the cylindrical portion.   The constant velocity universal joint according to any one of claims 1 to 4, wherein the protruding portion is provided at a central portion in the axial direction of the cylindrical portion.   The constant velocity universal joint according to any one of claims 1 to 4, wherein the protruding portion is provided at an axial end portion of the cylindrical portion.   The constant velocity universal joint according to claim 6, wherein the protruding portion is configured by folding back an axial end portion of the cylindrical portion toward the inner diameter side.   The constant velocity universal joint according to any one of claims 1 to 6, wherein a cross-sectional shape of the protrusion is V-shaped.   The constant velocity universal joint according to any one of claims 1 to 6, wherein a cross-sectional shape of the projecting portion is a convex curve bulging toward an inner diameter side.

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