JP2013189995A - Constant velocity joint - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a constant velocity joint suitably contracted when an axial load is applied from the outside.SOLUTION: A constant velocity joint 1 for connecting a first shaft 111 of a front side and a second shaft 112 of a rear side includes: a cylindrical outer ring member 10 having a rear side connected to the second shaft 112, a front side opened and a plurality of sliding grooves 13 formed at the inner peripheral surface of a peripheral wall 11; an inner ring unit 20 having a ball 22 sliding in the sliding groove 13; a shaft member 30 having a front side connected to the first shaft 111 and the inner ring unit 20 fixed to the rear side; and a collar 50 configured to be an annular member disposed in the front side opening of the outer ring member 10 to be larger in an inner peripheral surface toward the front side and for guiding the shaft member 30 and/or a member fixed to the shaft member 30 toward the center of the outer ring member when the outer ring member 10 and the shaft member 30 come close to each other in an axis direction.

Description

  The present invention relates to a constant velocity joint.

  A rear-wheel drive vehicle or a four-wheel drive vehicle in which an internal combustion engine (power source) is mounted on the front side of the vehicle body and the rear wheels are driven by the power is provided with a propulsion shaft (propeller shaft) at the lower center of the vehicle body. Through this, the power of the internal combustion engine (transmission) is transmitted to the rear wheels. Here, the propulsion shaft needs to be set to have a resonance point (resonating rotational speed) higher than the practical rotational speed range, and thus is divided by an appropriate length. For example, when divided into two, the propulsion shaft includes a first shaft on the front side (one side), a second shaft on the rear side (the other side), and a constant velocity joint that connects the first shaft and the second shaft. It is configured with. The constant velocity joint includes a double offset type, a tripod type, and the like.

  By the way, in order to suppress the impact on the passengers when the vehicle collides forward, an easily deformable region (crushable zone) is provided between the internal combustion engine and the passenger compartment, and the collision energy is absorbed in this crushable zone. There is technology to do. In this case, when the vehicle has a configuration including a propulsion shaft, the propulsion shaft becomes a support rod, the movement of the internal combustion engine and the transmission to the rear is inhibited, and the deformation of the vehicle body is inhibited, that is, the crusher. There is a risk that impact energy will be hardly absorbed in the bull zone.

  Therefore, a cap is detachably attached to the bottom wall portion of the outer ring member (outer race) constituting the constant velocity joint, and when the first shaft and the shaft member connected thereto are retracted at the time of a forward collision, the shaft member attaches the cap. A technique has been proposed in which the entire length of the propulsion shaft is shortened by pushing it off and causing the shaft member to enter the outer ring member (see, for example, Patent Document 1).

Japanese Patent No. 3958621

  However, since the propulsion shaft can be bent with a slider (ball, roller, etc.) constituting the constant velocity joint as a node, the propulsion shaft is bent, that is, an outer ring member and an inner ring member (inner ring member). When the first shaft tries to move backward while the shaft member integrated with the race is inclined, the shaft member and the parts (such as the inner ring) fixed to the shaft member are the end portions on the first shaft side of the outer ring member. There is a possibility that the propulsion shaft does not degenerate well.

  SUMMARY OF THE INVENTION An object of the present invention is to provide a constant velocity joint that suitably degenerates when an axial load is input from the outside.

  As means for solving the above-mentioned problem, the present invention is a constant velocity joint that connects the first shaft on one side and the second shaft on the other side, and is connected on the other side with the second shaft, A cylindrical outer ring member having an opening on one side and a plurality of sliding grooves formed on the inner peripheral surface of the peripheral wall, an inner ring unit having a slider that slides on the sliding groove, the first shaft, A ring member that is connected at the side and is provided at the opening on one side of the outer ring member, and the inner peripheral surface increases in diameter toward the one side. A guide member that guides the shaft member and / or a member fixed to the shaft member toward the center of the outer ring member when the outer ring member and the shaft member approach each other in the axial direction. This is a constant velocity joint.

  According to such a configuration, for example, when a load directed in the other direction in the axial direction is input to the shaft member and the outer ring member and the shaft member approach each other, even if the shaft member and the outer ring member are inclined, the shaft A member fixed to the member and / or the shaft member (in the embodiment described later, an inner ring, a stopper ring, etc.) is an annular guide member whose inner peripheral surface is increased in diameter toward one side, that is, toward the other side. Accordingly, the inner peripheral surface is a guide member having a reduced diameter, and is guided (guided) toward the center of the outer ring member. As a result, the shaft member and / or the member fixed to the shaft member are satisfactorily inserted into the outer ring member and submerged, and the constant velocity joint is suitably retracted.

  In the constant velocity joint, it is preferable that an inner diameter of the guide member is smaller than an inner diameter passing through a bottom surface of the sliding groove.

  According to such a configuration, since the inner diameter of the guide member is smaller than the inner diameter passing through the bottom surface of the sliding groove, the guide member protrudes radially inward from the bottom surface of the sliding groove when viewed in the axial direction. Here, the sliding groove is filled with grease for lubricating the sliding groove and the slider, but since the guide member protrudes from the bottom surface of the sliding groove in this way, It becomes difficult to leak outside. Thereby, the lubrication state of a sliding groove and a slider can be maintained favorable, and the durability improves.

  In the constant velocity joint, it is preferable that an inner diameter of the guide member is larger than an inner diameter passing through a portion of the peripheral wall portion where no sliding groove is formed.

  According to such a configuration, the shaft member and the parts fixed to the shaft member can sink into the outer ring member without getting over the guide member.

  Further, in the constant velocity joint, a boot for closing the gap between the peripheral wall portion and the shaft member and formed of an elastic body, and a part for attaching the boot to the outer ring member, A boot fixture having an outer fitting portion that is fitted to the peripheral wall portion, and the guide member is sandwiched between the outer fitting portion and the peripheral wall portion in a radial direction. Preferably it is.

  According to such a configuration, since the guide member is sandwiched between the outer fitting portion of the boot mounting tool and the peripheral wall portion of the outer ring member, the boot holder is favorably fixed to the outer ring member.

  In the constant velocity joint, the guide member is preferably a press-molded product.

  According to such a configuration, the guide member can be easily configured (manufactured).

  Moreover, in the constant velocity joint, it is preferable that the guide member includes a guide portion that is formed thicker than other portions and whose inner peripheral surface is increased in diameter toward one side.

  According to such a configuration, since the guide portion is formed to be thicker than other portions, the rigidity and impact resistance of the guide portion are higher than those of the other portions. Thereby, even if a large axial load is applied to the shaft member or the like, the shaft member or the like is favorably guided by the guide portion having high rigidity or the like.

  According to the present invention, it is possible to provide a constant velocity joint that suitably degenerates when an axial load is input from the outside.

It is a top view of the propulsion shaft concerning a 1st embodiment. It is a top view of the constant velocity joint which concerns on 1st Embodiment. It is an enlarged view of the top view of the constant velocity joint which concerns on 1st Embodiment. It is a front view of the outer ring member and collar concerning a 1st embodiment. It is an enlarged view of the top view of the constant velocity joint which concerns on 2nd Embodiment. It is an enlarged view of the top view of the constant velocity joint which concerns on 3rd Embodiment.

<< First Embodiment >>
A first embodiment of the present invention will be described with reference to FIGS.

≪Composition of propulsion shaft≫
A propulsion shaft 100 (propeller shaft) according to the present embodiment is mounted on a rear-wheel drive four-wheeled vehicle (vehicle), and transmits the power output from a transmission (not shown) disposed on the front side of the vehicle to the rear of the vehicle. This is a shaft that is transmitted to a final reduction gear (not shown) that is disposed at the center in the vehicle width direction, and extends in the front-rear direction and in the horizontal direction.

The propulsion shaft 100 has a two-piece structure (a two-part structure). The first shaft 111 on the front side (one side), the second shaft 112 on the rear side (the other side), the first shaft 111, and the first shaft A constant velocity joint 1 that connects the two shafts 112 and an intermediate bearing unit 60 that rotatably supports the propulsion shaft 100 at an intermediate position are provided.
However, the number of pieces (number of divisions) is not limited to this, and may be appropriately changed to a three-piece structure (three-division structure) or the like.

The first shaft 111 is a cylindrical part. A front end portion of the first shaft 111 is connected to an output shaft (not shown) of the transmission via a first universal joint 121 (cross joint or the like).
The second shaft 112 is a cylindrical part. The rear end portion of the second shaft 112 is connected to a drive pinion (not shown) of the final reduction gear via a second universal joint 122 (cross joint or the like).

≪Configuration of constant velocity joint≫
The constant velocity joint 1 is a joint that connects the rear end portion of the first shaft 111 and the front end portion of the second shaft 112, and is configured as a double offset type in the present embodiment.

  As shown in FIGS. 2 and 3, the constant velocity joint 1 includes an outer ring member 10, an inner ring unit 20 that slides in the outer ring member 10 in the axial direction, a shaft member 30, a boot 40, and a collar 50 (guide). Member).

<Outer ring member>
The outer ring member 10 (outer race) is a cylindrical part whose front side and rear side are open, and includes a peripheral wall part 11, a bottom wall part 12 formed on the rear side of the peripheral wall part 11 and having a through hole 12a at the center. It is equipped with. The rear side (the other side) of the bottom wall portion 12 is joined (connected) to the front end portion of the second shaft 112 by welding (friction welding or the like). As a result, the outer ring member 10 rotates integrally with the second shaft 112.

  On the inner peripheral surface of the peripheral wall portion 11, eight (a plurality of) sliding grooves 13 that extend in the axial direction and open on the front side are formed. The eight sliding grooves 13 are arranged at equal intervals in the circumferential direction. Each sliding groove 13 has a semicircular shape in a cross-sectional view in a ring section (see FIG. 4), and a ball 22 to be described later of the inner ring unit 20 slides or rolls.

  A shallow bottomed cylindrical cap 14 is detachably attached to the through hole 12a of the bottom wall portion 12. The outer diameter of the cap 14 (the inner diameter of the through hole 12 a) is formed smaller than the inner diameter of the cylindrical second shaft 112. Accordingly, when the first shaft 111 and the shaft member 30 are retracted at the time of a front collision, the cap 14 is detached from the bottom wall portion 12 and pushed out into the second shaft 112 by the rear end of the shaft member 30, thereby About 30 half (small diameter part 33 etc.) of 30 is inserted in the 2nd axis | shaft 112 favorably.

<Inner ring member>
The inner ring unit 20 includes a cylindrical inner ring member 21 (inner race), eight (plural) balls 22 (sliders), and a cylindrical cage 23.

  The inner ring member 21 has a thick cylindrical shape, and is formed with eight (plural) ball grooves 21a extending in the axial direction on the outer circumferential surface thereof and arranged at equal intervals in the circumferential direction. A part of the inner side in the radial direction of the ball 22 is in contact with the ball groove 21a (see FIG. 4).

  A hole spline is formed on the inner peripheral surface of the inner ring member 21, and the hole spline is fitted with a shaft spline formed on the outer peripheral surface of the shaft member 30. Thereby, the inner ring member 21 and the shaft member 30 are prevented from rotating relative to each other in the circumferential direction.

  The inner ring member 21 is sandwiched between a rear C-shaped stopper ring 24 and a front collar 25 in the axial direction. As a result, the inner ring member 21 and the small diameter portion 33 (shaft member 30) are prevented from moving relative to each other in the axial direction.

This will be described more specifically.
The stopper ring 24 is inserted into an annular groove 33 a formed on the outer peripheral surface of the small diameter portion 33 of the shaft member 30. Thus, the stopper ring 24 is fixed to the small diameter portion 33 in the axial direction.

  The collar 25 has an L shape in a sectional view and an annular shape (or a C shape) in an axial view. Between the collar portion 25a formed on the front side of the collar 25 and the small-diameter portion 33, a stopper ring 26 having a circular shape in a sectional view and an annular shape (or a C-shape) in an axial direction is attached. On the front side of the stopper ring 26, a raised portion 33b formed by partially protruding the outer peripheral surface of the small-diameter portion 33 is disposed. Normally, the raised portion 33b regulates the stopper ring 26 and the collar 25. Yes.

  On the other hand, when a backward load is applied to the shaft member 30 at the time of a forward collision, the stopper ring 26 rides on the raised portion 33b and the collar 25 expands in diameter, and the restriction by the stopper ring 26 and the collar 25 is released, and the small diameter The portion 33 is further inserted into the inner ring member 21, that is, the insertion of the small diameter portion 33 into the inner ring member 21 proceeds. Therefore, the rear side of the raised portion 33b (on the stopper ring 26 side) is an acute inclined surface so that the stopper ring 26 can easily ride.

  The cage 23 is fixed to the inner ring member 21 and is formed with eight (plural) holding holes 23a in the circumferential direction. Further, the outer peripheral surface of the cage 23 is formed in a spherical shape so that the cage 23 does not contact the outer ring member 10 even if the shaft member 30 is bent with respect to the outer ring member 10.

  The ball 22 is held in the holding hole 23a at the radial intermediate portion (see FIG. 4), and about 1/2 of the outer side in the radial direction is in spherical contact with the sliding groove 13. Thereby, the shaft member 30 and the outer ring member 10 can be bent with the ball 22 as a node.

  Further, the ball 22 slides or rolls in the sliding groove 13 so that the inner ring unit 20 and the outer ring member 10 are relatively movable in the axial direction. Note that grease (lubricating oil) is enclosed in the sliding groove 13 in order to prevent wear and seizure of the ball 22 and the sliding groove 13 due to sliding or the like.

<Shaft member>
The shaft member 30 is a solid or hollow, integrally formed rod-like component, and includes a large diameter part 31, a medium diameter part 32, and a small diameter part 33 from the front side toward the rear side.

  The front side (one side) of the large-diameter portion 31 is joined (connected) to the rear end portion of the first shaft 111 by welding (friction welding or the like). As a result, the shaft member 30 rotates integrally with the first shaft 111.

  The intermediate diameter portion 32 is a portion that is rotatably supported by the intermediate bearing unit 60, and a bearing 61 described later is intermediately fitted to the intermediate diameter portion 32. Further, an enlarged diameter portion 34 that is enlarged in steps is formed on the front side of the intermediate diameter portion 32, and the enlarged diameter portion 34 is in contact with the front side of the inner ring of the bearing 61.

  The small diameter portion 33 is designed to have a length that is about ½ of the entire shaft member 30. Thus, the shaft member 30 can be satisfactorily submerged in the outer ring member 10 at the time of a forward collision. As described above, the inner ring unit 20 is fixed to the rear side (the other side) of the small diameter portion 33.

<Boots>
The boot 40 is an annular part, and seals the gap between the front opening of the outer ring member 10 and the shaft member 30, and (1) prevents the grease in the outer ring member 10 from flowing out to the outside. (2) This is a component that prevents intrusion of water, dust, muddy water and the like into the outer ring member 10 from the outside.

  The boot 40 includes a boot large diameter portion 41, a boot small diameter portion 42, and a boot bending portion 43. The boot large-diameter portion 41, the boot small-diameter portion 42, and the boot bending portion 43 are made of rubber (elastic body) and are integrally formed.

  The boot large-diameter portion 41 is fixed to the outer ring member 10 via a cylindrical adapter 44 (boot fitting). Specifically, the front end portion of the boot large-diameter portion 41 is inserted and fixed to a push-back portion (a part) on the front side of the adapter 44, and the rear end portion of the adapter 44 is fitted to the outer ring member 10. .

  The adapter 44 is a part for attaching the boot 40 to the outer ring member 10, and has a cylindrical outer fitting part 44a fitted on the outer ring member 10 on the rear side, and a radially inward direction from the front end of the outer fitting part 44a. And a ring-shaped part 44b that exhibits a ring shape when viewed in the axial direction. An O-ring 45 is interposed between the outer fitting portion 44a and the outer ring member 10 to enhance the sealing performance. The radial length of the ring-shaped portion 44b is substantially equal to the thickness of the peripheral wall portion 11 in the portion where the sliding groove 13 of the outer ring member 10 is formed, and the ring-shaped portion 44b is the ring-shaped portion of the collar 50 in the axial direction. 52 is pressed against the outer ring member 10 side.

  The boot small diameter portion 42 has a smaller diameter than the boot large diameter portion 41 and is fitted to the small diameter portion 33 of the shaft member 30. The boot small-diameter portion 42 is fastened by a boot band 46 from the outside in the radial direction, and the boot small-diameter portion 42 and the small-diameter portion 33 of the shaft member 30 are in good contact.

  The boot bending portion 43 is formed between the front end of the boot large-diameter portion 41 and the front end of the boot small-diameter portion 42, has a horizontal U shape in a cross-sectional view, and is a bendable portion. Thereby, the boot large diameter part 41 and the boot small diameter part 42 can change a relative position freely in an axial direction and a radial direction.

<Color>
The collar 50 is an annular press-molded product obtained by press-molding a metal cylindrical body, and is provided in the opening on the front side of the outer ring member 10. The collar 50 includes a base end portion 51 (mounting portion) that has a cylindrical shape on the rear side (the outer ring member 10 side), and a ring shape that extends radially inward from the front end of the base end portion 51 and has a ring shape when viewed in the axial direction. And a guide portion 53 extending from the radially inner end of the ring-shaped portion 52 to the front side (one side).

The base end portion 51 is fitted into a mounting groove 11 a formed in an annular shape on the front side of the outer peripheral surface of the peripheral wall portion 11, and is externally fitted to the peripheral wall portion 11. Further, the base end portion 51 is sandwiched between the peripheral wall portion 11 and the outer fitting portion 44 a constituting the adapter 44 in the radial direction. The ring-shaped part 52 is sandwiched between the peripheral wall part 11 and the ring-shaped part 52 constituting the adapter 44 in the axial direction.
Thus, since the collar 50 is sandwiched in the circumferential direction and the axial direction, the collar 50 is positioned and fixed to the outer ring member 10.

  The guide portion 53 is a funnel-shaped portion that extends while increasing its inner diameter from the radially inner end of the ring-shaped portion 52 toward the front side. As a result, when the first shaft 111 and the shaft member 30 move backward during a frontal collision, the center axis of the shaft member 30 and the center axis of the outer ring member 10 are shifted, and the shaft member 30 is inclined with respect to the outer ring member 10. Even if it does, the middle diameter part 32 of the shaft member 30 and the stopper piece 66 described later are guided by the guide part 53 toward the central axis of the outer ring member 10, and the middle diameter part 32 and the stopper piece 66 are guided by the outer ring member 10. It is designed to dive well inside.

<Relationship between inner diameter of collar and inner diameter of outer ring member>
As shown in FIG. 4, the inner diameter D1 of the collar 50 is designed to be smaller than the inner diameter D2 passing through the bottom surface of the sliding groove 13 (D1 <D2). That is, the collar 50 protrudes radially inward from the bottom surface of the sliding groove 13, and the collar 50 closes the front opening of the sliding groove 13.

  Thereby, the ball 22 is prevented from coming out of the sliding groove 13. Therefore, the inner ring unit 20 is prevented from coming out of the outer ring member 10 when the constant velocity joint 1 is transported or assembled with the first shaft 111.

  Further, even if the centrifugal force acts on the grease enclosed in the outer ring member 10 by the rotation of the propulsion shaft 100 and this grease moves forward along the bottom surface of the sliding groove 13, it is blocked by the collar 50, The grease is likely to stay in the outer ring member 10. Therefore, the lubrication state between the sliding groove 13 and the ball 22 is easily maintained well.

Further, the inner diameter D1 of the collar 50 is designed to be larger than the inner diameter D3 passing through the portion of the peripheral wall portion 11 where the sliding groove 13 is not formed (D3 <D1). That is, the collar 50 does not protrude from the peripheral wall portion 11 in the radial direction.
As a result, the inner ring 62 and the stopper piece 66 of the shaft member 30 that is retracted can get into the outer ring member 10 without getting over the collar 50 when the vehicle collides forward.

<Intermediate bearing unit>
The intermediate bearing unit 60 is a unit that rotatably supports the propulsion shaft 100 at an intermediate position. The intermediate bearing unit 60 includes a bearing 61, an inner ring 62, a mount 63, an outer ring 64, a collar 65, a stopper piece 66, and a stopper member 67.

  The bearing 61 is constituted by a shielded radial ball bearing, and is fitted on the medium diameter portion 32 of the shaft member 30. The front side of the inner ring is in contact with the aforementioned enlarged diameter portion 34, and the rear side of the inner ring is in contact with the stopper piece 66. Thereby, the bearing 61 is fixed to the shaft member 30 in the axial direction.

  The stopper piece 66 is a cylindrical part that prevents the bearing 61 from coming out backward, and is press-fitted and fixed to the medium diameter portion 32.

  The outer diameter of the stopper piece 66 is designed to be smaller than the inner diameter D3 of the outer ring member 10 so that the stopper piece 66 can be satisfactorily embedded in the outer ring member 10 at the time of forward collision.

  The inner ring 62 is a cylindrical part that fits around the bearing 61. The rear side of the inner ring 62 has a reduced diameter due to a step difference, and the reduced diameter portion is in contact with the rear side of the outer ring of the bearing 61. The stopper member 67 has a horizontal U shape with a front side opened in a cross-sectional view, is press-fitted and fixed inside the inner ring 62 on the front side of the bearing 61, and is in contact with the front side of the outer ring of the bearing 61.

  A labyrinth member 68 (dust cover) that is press-fitted and fixed to the enlarged diameter portion 34 is disposed on the front side of the stop member 67, and the labyrinth member 68 and the stop member 67 constitute a labyrinth structure. That is, the labyrinth member 68 has a horizontal U shape with an open rear side, and the front side of the stop member 67 is loosely inserted into the opening at a predetermined interval. A passage formed between the stopper member 67 and the labyrinth member 68 and leading from the outside to the bearing 61 meanders, and external water or the like hardly reaches the bearing 61.

  The outer diameter of the rear side of the inner ring 62 is designed to be smaller than the inner diameter D3 of the outer ring member 10, so that the inner ring 62 can be well embedded in the outer ring member 10 at the time of a front collision.

  The mount 63 (anti-vibration rubber) is an annular part integrally formed of rubber (elastic body) and is provided between the inner ring 62 and the outer ring 64 and is vulcanized to the inner ring 62 and the outer ring 64. It is glued. Thereby, the vibration of the inner ring 62 (shaft member 30) is absorbed and attenuated by the mount 63, and is difficult to be transmitted to the outer ring 64 (vehicle body).

  The outer ring 64 is a part having a cylindrical shape (annular shape) having a larger diameter than the inner ring 62, and is arranged at the same center with a predetermined interval on the radially outer side of the inner ring 62. A cylindrical collar 65 is fixed outside the outer ring 64. A bracket (not shown) that is substantially C-shaped when viewed in the axial direction is fixed to the outer side of the collar 65, and this bracket is fixed to the lower portion of the vehicle body (outside) (not shown).

≪Function and effect of constant velocity joint (propulsion shaft) ≫
According to such a constant velocity joint 1 (propulsion shaft 100), the following effects are obtained.
When the vehicle collides forward, a backward load acts on an internal combustion engine and a transmission (not shown) mounted under the bonnet, and a backward load acts on the first shaft 111 and the shaft member 30, the small diameter portion 33. The inner ring unit 20 moves backward in the outer ring member 10, the shaft member 30 and the outer ring member 10 approach in the axial direction, and the cage 23 collides with the bottom wall portion 12. When a further backward load is applied, the stopper ring 26 and the collar 25 get over the raised portion 33b, and the axial restriction between the small diameter portion 33 and the inner ring member 21 is released.

  Then, the inner ring member 21 that is in contact with the bottom wall portion 12 via the cage 23 is left as it is, and the small-diameter portion 33 (the shaft member 30) is further retracted, the cap 14 is pushed out, and the second shaft 112 is inserted. Plugged in. In parallel with this, the rubber boot 40 and the mount 63 are broken, the medium diameter portion 32, the inner ring 62 and the stopper piece 66 of the shaft member 30 are inserted into the outer ring member 10, and the first shaft 111 is also inserted. Retreat well.

  In this case, even if the shaft member 30 is inclined with respect to the outer ring member 10, that is, even if the central axis of the shaft member 30 is oblique with respect to the central axis of the outer ring member 10, the inner ring 62 and After the stopper piece 66 and the like are in contact with the guide portion 53 of the collar 50 and are guided (guided) toward the center of the outer ring member 10 while sliding, the inner ring 62 and the stopper piece 66 and the like are guided to the outer ring member 10. Dive into.

  In this way, the propulsion shaft 100 retracts well in the front-rear direction, so that the propulsion shaft 100 does not become a support rod, and the internal combustion engine and the transmission (not shown) retract favorably. Thereby, the impact energy is satisfactorily absorbed in the crushable zone formed between the internal combustion engine and the transmission and the passenger compartment.

≪Modification≫
As mentioned above, although one Embodiment of this invention was described, this invention is not limited to this, For example, you may change as follows and may combine with embodiment mentioned later suitably.

  In the above-described embodiment, the configuration in which the shaft member 30 is disposed on the front side and the outer ring member 10 is disposed on the rear side and power is input to the front shaft member 30 is exemplified. A configuration may be employed in which power is input to the outer ring member 10 by being disposed on the member 30.

<< Second Embodiment >>
Next, a second embodiment of the present invention will be described with reference to FIG. In addition, a different part from 1st Embodiment is demonstrated.

  In the second embodiment, the base end portion 51 of the collar 50 is fixed not on the outer side of the peripheral wall portion 11 constituting the outer ring member 10 (see FIG. 3) but on the inner side. An annular mounting groove 11b having a diameter larger than that of the sliding groove 13 is formed at the edge of the front opening of the peripheral wall portion 11, and the base end portion 51 is fitted in the mounting groove 11b.

  The ring-shaped portion 52 of the collar 50 is disposed in the outer ring member 10, that is, disposed on the rear side of the front end surface of the outer ring member 10.

  With this configuration, since the ring-shaped portion 52 is disposed in the outer ring member 10, the protruding length of the guide portion 53 from the outer ring member 10 is shortened by the thickness of the ring-shaped portion 52. As a result, the front end of the guide portion 53 moves to the rear side by the thickness of the ring-shaped portion 52, so that the guide portion 53 and the boot 40 do not easily interfere with each other.

«Third embodiment»
Next, a third embodiment of the present invention will be described with reference to FIG. In addition, a different part from 1st Embodiment is demonstrated.

In the third embodiment, a collar 70 that is a forged product is provided instead of the collar 50 that is a press-molded product (see FIG. 3).
Similar to the collar 50, the collar 70 includes a base end portion 71, a ring-shaped portion 72, and a guide portion 73.
However, the collar 70 is not limited to a forged product, but may be obtained by, for example, cutting a sintered alloy or a bar material.

  The guide portion 73 is formed to be thicker than the guide portion 53 (see FIG. 3), and is formed to be thicker than the base end portion 71 and the ring-shaped portion 72, and its rigidity is enhanced. That is, the guide part 53 has an extremely short and thick cylindrical shape, and its inner peripheral surface gradually increases in diameter toward the front side.

  Thereby, the guide part 73 becomes difficult to deform | transform rather than the guide part 53, for example, becomes difficult to open to radial direction outer side. Therefore, even if the collision load is large and the shaft member 30 is largely inclined with respect to the outer ring member 10, the inner ring 62, the stopper piece 66, etc. are guided by the guide portion 73 and sink into the outer ring member 10. Can do.

DESCRIPTION OF SYMBOLS 1 Constant velocity joint 10 Outer ring member 11 Peripheral wall part 13 Sliding groove 20 Inner ring unit 21 Inner ring member 22 Ball (slider)
30 Shaft member 40 Boot 44 Adapter (boot fitting)
44a Outer fitting part 50, 70 Color (guide member)
53, 73 Guide portion 60 Intermediate bearing unit 100 Propulsion shaft 111 First shaft 112 Second shaft D1 Inner diameter of collar D2 Inner diameter of bottom surface of sliding groove D3 Inner diameter of peripheral wall portion

Claims (6)

A constant velocity joint connecting the first shaft on one side and the second shaft on the other side,
A cylindrical outer ring member that is connected to the second shaft on the other side, has one side opened, and has a plurality of sliding grooves formed on the inner peripheral surface of the peripheral wall portion;
An inner ring unit having a slider that slides in the sliding groove;
A shaft member connected to the first shaft on one side and the inner ring unit fixed to the other side;
An annular member that is provided in an opening on one side of the outer ring member and has an inner peripheral surface that increases in diameter toward the one side, and when the outer ring member and the shaft member approach each other in the axial direction, A guide member for guiding a shaft member and / or a member fixed to the shaft member toward the center of the outer ring member;
A constant velocity joint characterized by comprising: The constant velocity joint according to claim 1, wherein an inner diameter of the guide member is smaller than an inner diameter passing through a bottom surface of the sliding groove. The constant velocity joint according to claim 1 or 2, wherein an inner diameter of the guide member is larger than an inner diameter passing through a portion of the peripheral wall portion where no sliding groove is formed. A boot formed of an elastic body and closing a gap between the peripheral wall portion and the shaft member;
A part for attaching the boot to the outer ring member, the boot being fixed to a part of the boot, and a boot fitting having an outer fitting part fitted on the peripheral wall part,
With
The constant velocity joint according to any one of claims 1 to 3, wherein the guide member is sandwiched between the outer fitting portion and the peripheral wall portion in a radial direction. The constant velocity joint according to any one of claims 1 to 4, wherein the guide member is a press-molded product. 5. The guide member according to claim 1, wherein the guide member includes a guide portion that is formed thicker than other portions and has an inner peripheral surface that increases in diameter toward one side. Constant velocity joint described in 1.

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