JPH08184326A - Constant velocity universal joint - Google Patents

Abstract

PURPOSE: To provide a constant velocity universal joint which can exactly secure uniform movability and can be used at a large joint angle. CONSTITUTION: This invention relates to a constant velocity universal joint A1 which has cruciform joints 12 and 14 at both ends of an intermediate shaft 11, which are symmetrical to the datum face S which orthogonally crosses the axis line L1 of the intermediate shaft 11 and includes the intermediate point between these cruciform joints 12 and 14, and is connected to an input shaft 13 and output shaft 15 through the cruciform joints 12 and 14 respectively to connect the input shaft 13 and output shaft 15 so that torque can be transmitted to each other. Therefore, this constant velocity universal joint A1 connects the input shaft 13 and output shaft 15 through interlock mechanisms 20 which are rotatably assembled to the outer circumference of their shaft ends and arranged outside the intermediate shaft 11, permit their rotation around their respective axis lines L3 and L5 and can change their respective joint angles θi and θo to the intermediate shaft 11 in symmetrical relation.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a constant velocity universal joint which is used for a part of a steering shaft or a drive shaft of a vehicle and which connects an input shaft and an output shaft so that torque can be transmitted.

[0002]

2. Description of the Related Art As one of constant velocity universal joints of this type, cross joints are provided at both ends of an intermediate shaft, respectively, and are symmetrical with respect to a reference plane orthogonal to the axis of the intermediate shaft, including a midpoint between the two cross joints. , Which is connected to the input shaft and the output shaft at each cross joint and connects the input shaft and the output shaft so that torque can be transmitted. For example, it is disclosed in Japanese Utility Model Laid-Open No. 59-137420. .

[0003]

By the way, in the constant velocity universal joint of the above publication, a spherical body formed at one shaft end of the input shaft and the output shaft and a cylindrical hole formed at the other shaft end can slide. When the joint angle of the input shaft with respect to the intermediate shaft changes, the joint angle of the output shaft with respect to the intermediate shaft also changes in conjunction with each other.
Since the center of the sphere moves in an arc as the joint angle changes, the joint angle on the input shaft side and the joint angle on the output shaft side do not become exactly the same except at a specific position, and the constant velocity of the universal joint is reduced. It cannot be secured exactly. Also,
In this constant velocity universal joint, increasing the joint angle causes interference between the shaft end forming the sphere and the shaft end forming the cylindrical hole, or between the shaft end forming the cylindrical hole and the intermediate shaft. The universal joint cannot be used as a large joint angle. The present invention has been made in view of the above problems, and an object thereof is to provide a constant velocity universal joint that can accurately ensure constant velocity and can be used as a large joint angle. It is in.

[0004]

In order to achieve the above-mentioned object, in the present invention, a cross joint is provided at each end of the intermediate shaft, and a reference crossing the axis of the intermediate shaft is included, including the intermediate points between the two cross joints. In a constant velocity universal joint that has plane symmetry with respect to a plane and is connected to an input shaft and an output shaft at each cross joint, and connects the input shaft and the output shaft so that torque can be transmitted, the input shaft and the output shaft The shafts are rotatably assembled to the outer circumferences of the respective shaft ends and arranged outside the intermediate shafts to allow rotation around the respective axial lines, and the respective joint angles with the intermediate shafts are changed in a symmetrical relationship. Connected by possible interlocking mechanism.

The interlocking mechanism is rotatably mounted on the outer periphery of the shaft end of the input shaft, and has an input side holder that allows rotation around the axis of the input shaft, and an input shaft holder that is orthogonal to the axis of the input shaft. Side input gear that is formed in an arc shape centered on the input side rotation axis passing through the joint center of the cross joint on one side and integrally provided on the input side holder, and rotates on the outer circumference of the shaft end of the output shaft. An output side holder that is assembled as much as possible and that allows rotation around the axis of the output shaft, and an input side rotation axis that is orthogonal to the axis of the output shaft and passes through the joint center of the cross joint on the output shaft side. Output gear that is formed in an arc shape centered on an output rotation axis parallel to the output gear and that is provided integrally with the output holder and that meshes with the input gear at an intermediate portion between the cross joints. It is desirable to have a configuration including.

Further, it is desirable to provide an urging means for urging the input side gear and the output side gear toward each other toward the meshing portion in the radial direction so as to elastically mesh with each other. Further, it is desirable to provide a regulation means for regulating the movement of the input side gear and the output side gear in the tooth width direction. Alternatively, an engaging portion that engages with the input side gear and the output side gear to allow rotation of the both gears, and the input side gear and the output side gear are radially attached to each other toward the meshing portion. The input side gear and the output side are provided by a locking member having a spring portion that urges and elastically meshes with each other, and a facing portion that restricts movement of the input side gear and the output side gear in the tooth width direction. It is desirable to connect gears.

[0007]

In the constant velocity universal joint according to the present invention, the input shaft and the output shaft are rotatably assembled to the outer circumferences of their respective shaft ends and are arranged outside the intermediate shaft to rotate about their respective axes. It is connected by an interlocking mechanism that allows it and changes each joint angle with the intermediate shaft in a symmetrical relationship, and the interlocking mechanism is arranged so as to cover the connecting portion of the input shaft and the output shaft via the intermediate shaft from the outside. Therefore, it is possible to easily set a configuration in which the interlocking mechanism does not interfere with the input shaft, the intermediate shaft, and the output shaft even when each joint angle is increased, and it is possible to use a large joint angle. Further, since the input shaft and the output shaft are changed by the interlocking mechanism so that each joint angle with the intermediate shaft is changed in a symmetrical relationship, all the torque transmission members such as the input shaft, the intermediate shaft, the output shaft and the double cross joint of the universal joint are changed. Maintains a plane-symmetrical arrangement with respect to the reference plane (constant velocity surface) orthogonal to the axis of the intermediate shaft, including the intermediate point between both cross joints, at any joint angle, and accurately maintains the uniform velocity in any state. Can be secured.

When the interlocking mechanism comprises the input side holder, the input side gear, the output side holder and the output side gear, the universal joint can be constructed simply and at low cost. When one joint angle changes by a predetermined amount, the same rotation is transmitted from one gear to the other gear due to the change of the joint angle, and the other joint angle is changed by a predetermined amount. Further, the input side gear is formed in an arc shape centered on the input side rotation axis passing through the joint center of the cross joint on the input shaft side and orthogonal to the axis line of the input shaft, and the output side gear is the axis line of the output shaft. Is formed in an arc shape centered on the output side rotation axis passing through the joint center of the cross joint on the output shaft side, and these gears mesh with each other at an intermediate portion between the two cross joints. Therefore, the distance between both cross joints is equal to the sum of the pitch circle radii of each gear (pitch circle diameter), and when changing the joint angle, each holder does not move integrally with each shaft in the axial direction. Therefore, no thrust force is generated between each holder and each shaft, and the structure of the shaft support of each holder can be made simple and inexpensive.

Further, when an urging means for elastically urging the input side gear and the output side gear toward the meshing portion to urge each other in the radial direction is provided, the meshing portion of both gears is engaged. It is possible to suppress the rattling noise by eliminating the backlash. Further, when a regulating means for regulating the movement of the input side gear and the output side gear in the tooth width direction is provided, even if a couple force is input to the interlocking mechanism, the meshing between the input side gear and the output side gear will occur. It does not disengage in the tooth width direction, and the engagement between the input side gear and the output side gear can be guaranteed.

Further, an engaging portion that engages with the input side gear and the output side gear to allow rotation of the both gears, and a diameter of the input side gear and the output side gear toward each other toward the meshing portion. The input side gear by a locking member having a spring part that biases in a direction to elastically mesh with each other, and a facing part that restricts the movement of the input side gear and the output side gear in the tooth width direction. When the output side gear is connected, both functions of the biasing means and the regulating means described above can be exerted by one locking member, and the generation of rattling noise is suppressed with a simple and inexpensive structure. In addition, the meshing of the input side gear and the output side gear can be guaranteed.

[0011]

Embodiments of the present invention will be described below with reference to the drawings. 1 and 2 show a first embodiment of a constant velocity universal joint according to the present invention. In the constant velocity universal joint A1 of the first embodiment, an input is made at one end of an intermediate shaft 11 via a cross joint 12. The shaft 13 is connected, and the output shaft 15 (formed in the same shape as the input shaft 13) through the cross joint 14 (formed in the same shape as the cross joint 12) at the other end of the intermediate shaft 11. Are connected, and the cross joint 1
Reference numerals 2 and 14 are arranged symmetrically with respect to a reference plane S orthogonal to the axis L1 of the intermediate shaft 11 including an intermediate point between the two cross joints 12 and 14, and the input shaft 13 and the output shaft 15 can transmit torque. Are linked to. Also, this constant velocity universal joint A
1, the interlocking mechanism 20 for changing the joint angle θi of the input shaft 13 with respect to the intermediate shaft 11 and the joint angle θo of the output shaft 15 with respect to the intermediate shaft 11 in a symmetrical relationship.
Is provided between the input shaft 13 and the output shaft 15.

The interlocking mechanism 20 is rotatably assembled to the outer circumference of the shaft end of the input shaft 13 via a bearing B1 and allows the input shaft holder 21 to rotate about the axis L3.
And is formed in an arc shape centered on the input side rotation axis L2 that is orthogonal to the axis L3 of the input shaft 13 and passes through the joint center O1 of the cross joint 12 on the input shaft side, and is integrally provided on the input side holder 21. A pair of input side gears 22, an output side holder 23 that is rotatably mounted on the outer circumference of the shaft end of the output shaft 15 via a bearing B2, and that allows the output shaft 15 to rotate about the axis L5; The output is formed in an arc shape centered on an output side rotation axis L4 that is orthogonal to the axis L5 of 15 and passes through the joint center O2 of the cross joint 14 on the output shaft side and is parallel to the input side rotation axis L2. The side holder 23 is provided integrally with a pair of output gears 24 that mesh with the respective input gears 22 at an intermediate portion between the cross joints 12 and 14.

The input side gear 22 integrally provided in the input side holder 21 and the output side gear 24 integrally provided in the output side holder 23 are composed of the intermediate shaft 11, the universal joint 12, the input shaft 13, and the universal shaft 11. The joint 14 and the output shaft 15 are configured so as to be detachable in a connected state, and each bearing B1,
B2 is a stepped inner hole 21a, 23a of each holder 21, 23
(See FIG. 4) It is configured to be assembled in advance. Further, in the present embodiment, as shown in FIG. 3, each tooth of each gear 22, 23 has a stepped inner hole 21a, 23.
axis of a (axis L of each axis 13 and 15 when assembled)
3 and L5), the position is shifted by 1/4 · P (it is also possible to shift by 1/2 · P. P: angle formed by adjacent teeth of gear). The gears 22 and 23 have the same specifications, and parts are made common. The axial movement of the bearings B1 and B2 is carried out by attaching and detaching the annular flanges 13a and 15a provided at the shaft ends of the shafts 13 and 15 and the annular grooves 13b and 15b formed at the shaft ends of the shafts 13 and 15, respectively. It is designed to be regulated by the rings C1 and C2 which are assembled as possible (see FIGS. 2, 5 and 6).

In the constant velocity universal joint A1 constructed as described above, when the input shaft 13 is rotated in the state shown in FIGS. 1 and 2, the intermediate shaft 11 is rotated via the universal joint 12, and The output shaft 15 is rotated via the universal joint 14 as the intermediate shaft 11 rotates, and the rotation and torque of the input shaft 13 are transmitted to the output shaft 15. During this torque transmission,
Both holders 21 and 23 of the interlocking mechanism 20 and both gears 22 and 24
Accordingly, all the torque transmitting members such as the input shaft 12, the intermediate shaft 11, the output shaft 15, the both cross joints 12 and 14 are set to the reference plane S.
Since the plane-symmetrical arrangement is maintained with respect to, no torque fluctuation occurs during torque transmission.

By the way, in the state shown in FIGS. 1 and 2, for example, when the input shaft 13 is tilted about the axis L2 to change the joint angle θi of the input shaft 13 with respect to the intermediate shaft 11 by a predetermined amount, the input shaft 13 is tilted. Accordingly, the input side gear 22 has an axis L
The output side gear 24 is rotated about the axis L4 by the same amount by rotating about the axis L4 by two turns to change the joint angle θo of the output shaft 15 with respect to the intermediate shaft 11 by a predetermined amount. Therefore, even after the joint angle is changed, the input shaft 12, the intermediate shaft 11,
The torque transmitting members such as the output shaft 15 and the two cross joints 12 and 14 are maintained in plane symmetry with respect to the reference plane S, and the constant velocity can be accurately ensured in any state.

Further, both holders 21, 23 of the interlocking mechanism 20.
The two gears 22 and 24 are rotatably assembled to the shaft end outer circumferences of the input shaft 13 and the output shaft 15, respectively, and are arranged outside the intermediate shaft 11, and the axis lines L3 and L of the input shaft 13 and the output shaft 15 are arranged.
Each of the five rotations is allowed, and the intermediate shaft 1
Since it is arranged so as to cover the connecting portion of the input shaft 13 and the output shaft 15 through the outer side from each other, each joint angle θ
Even when i and θo are increased, the input shaft 13 and the intermediate shaft 11
Also, a configuration that does not interfere with the output shaft 15 can be easily set, and it can be used as a large joint angle.

Further, the interlocking mechanism 20 includes the input side holder 2
1, the input side gear 22, the output side holder 23, and the output side gear 24, the universal joint A1 can be configured simply and inexpensively, and the intermediate shaft 11, the universal joint 12, the input shaft 13, and the universal joint 14 can be formed. Since the output shaft 15 is connected and detachable,
Excellent in assembling and maintainability.

The input side gear 22 is orthogonal to the axis L3 of the input shaft 13 and the joint center O of the cross joint 12 on the input shaft side.
1 is formed in an arc shape centered on the input side rotation axis L2 passing through 1, and the output side gear 24 is orthogonal to the axis L5 of the output shaft 15 and the joint center O of the cross joint 14 on the output shaft side.
2 is formed in an arc shape centering on the output side rotation axis L4 passing through 2, and these gears 22 and 24 are formed in the double cross joint 1
Since the gears 22 and 14 mesh with each other at an intermediate portion, the distance between the two cross joints 12 and 14 is equal to that obtained by combining the pitch circle radii of the gears 22 and 24 (pitch circle diameter). When changing the corners, the holders 21 and 23 do not move axially on the shafts 13 and 15, respectively. Therefore, no thrust force is generated between the holders 21 and 23 and the shafts 13 and 15, and inexpensive bearings can be used as the bearings B1 and B2.

FIG. 7 shows a second embodiment of the constant velocity universal joint according to the present invention, which is a constant velocity universal joint A2 of the second embodiment.
The holding plate 25 for preventing disengagement on the outer side (tooth width direction) of each gear 22, 24,
Since 26 are welded to each other, even if a couple force is input to the interlocking mechanism 20, the meshing of the gears 22 and 24 does not deviate in the tooth width direction, and the meshing of the gears 22 and 24 can be guaranteed. . Since other configurations are the same as the configurations of the first embodiment described above, the same members are designated by the same reference numerals, and the description thereof will be omitted. Further, the operation and effect of the second embodiment is substantially the same as the operation and effect of the first embodiment, and the description thereof will be omitted.

Further, in order to prevent disengagement of the gears 22 and 24 from the outside, the gears 22 and 24 are helical gears, and the directions of the teeth of the two teeth of the gears 22 and 24 are different. Can also be formed in the opposite direction.
By doing so, a function of preventing the gears from being disengaged from each other is created, and it is not necessary to add new parts.

FIG. 8 shows a third embodiment of the constant velocity universal joint according to the present invention, which is a constant velocity universal joint A3 of the third embodiment.
In the above, the tension coil spring 27 is provided between the locking pieces 25a and 26a provided on the holding plates 25 and 26.
Is attached to the tension coil spring 27
The two gears 22 and 24 can be elastically meshed with each other, and the rattling noise can be suppressed by eliminating the backlash at the meshing portion. By disposing the locking pieces 25a and 26a near the centers of the gears 22 and 24 so that the attachment length of the tension coil spring 27 hardly changes even when the joint angle is changed, when the joint angle is changed. The spring force of the tension coil spring 27 hardly changes, and smooth operation is guaranteed. When the tension coil spring 27 is provided, the retaining rings C1 and C2 attached to the shafts 13 and 15 are unnecessary, and the annular grooves 13b and 15b of the shafts 13 and 15 are also unnecessary. Since the other configurations and effects are the same as those of the second embodiment, the same members are designated by the same reference numerals and the description thereof will be omitted.

FIG. 9 shows a fourth embodiment of the constant velocity universal joint according to the present invention, which is a constant velocity universal joint A4 of the fourth embodiment.
In the first embodiment described above,
Retaining rings C1 and C2 attached to 5
Instead of the annular grooves 13 formed at the shaft ends of the shafts 13 and 15, respectively.
The disc springs D1 and D2 that are detachably attached to b are used. In this embodiment, the disc springs D1 and D2 can elastically mesh the two gears 22 and 24 with each other, thereby eliminating rattling at the meshing portions and suppressing rattling noise. Since the other configurations and effects are the same as those of the first embodiment, the same members are designated by the same reference numerals and the description thereof will be omitted.

FIG. 10 shows a fifth example of the constant velocity universal joint according to the present invention.
An embodiment is shown and a constant velocity universal joint A of the fifth embodiment is shown.
In FIG. 5, a torsion spring 28 (may be a mere wire spring or a leaf spring) is attached between both gears 22 and 24.
The two gears 22 and 24 can be elastically meshed with each other at 8, and rattling noise can be suppressed by eliminating rattling at the meshing portion, and the torsion spring 2
8, it is possible to prevent disengagement of the gears 22, 24 from the outside. Since the other configurations and effects are the same as those of the first embodiment, the same members are designated by the same reference numerals and the description thereof will be omitted.

In the fifth embodiment of FIG. 10 described above,
A torsion spring 28 is attached between the gears 22 and 24 to suppress the generation of rattling noise and
Although the engagement of 24 is prevented from being disengaged, it is also possible to obtain the same effect as that of the fifth embodiment of FIG. 10 by adopting the interlocking mechanism 20 shown in FIG. Is. Interlocking mechanism 2 shown in FIG.
0 is the same as the pair of input side gears 22 integrally provided on the input side holder 21 assembled to the input shaft similarly to the input side holders of the above-mentioned respective embodiments, and the output side holder of the above-mentioned respective embodiments. And a pair of output gears 24 integrally provided on an output side holder 23 that is assembled to the output shaft.
A locking member 29 for connecting the locking members 2 and 24 is provided, and mounting holes 22a and 24a for mounting the locking member 29 are formed in the gears 22 and 24, respectively, as shown in FIG.

The locking member 29 is formed by processing an iron plate as shown in FIGS. 11, 13 and 14, and part of the mounting holes 22a and 24a of the gears 22 and 24, respectively. A substantially semi-cylindrical shape that elastically engages with (a portion formed in an arc shape centering on the rotation axis L2, L4 of each gear 22, 24) to allow the rotation of both gears 22, 24. Engaging portions 29a and 29b, mountain-shaped spring portions 29c that elastically urge the gears 22 and 24 toward the meshing portions in the radial direction to elastically engage each other, and the spring portions 29c and the engaging portions. 29
Outside of each gear 22, 24 between a and 29b (tooth width direction)
Facing portions 29d and 29e for restricting the movement of the gears 22 and 2 to the end portions of the engaging portions 29a and 29b.
4 is a semi-circular locking portion 29 which is slidably locked to the side surface.
a1 and 29b1 are formed. This locking member 29
Are mounting holes 22a of the gears 22 and 24 in the state of FIG.
The engaging parts 29a and 29b are fitted to the upper part of 24a and then moved downward as shown by the small arrow in FIG. 11, so that the parts are assembled as shown in FIG. In this state, the gears 22 and 24 are urged in the radial direction toward the meshing portions as indicated by the large arrows.

The interlocking mechanism 2 of FIG. 11 configured as described above.
In 0, the gears 22 and 24 are connected by the locking member 29 having the engaging portions 29a and 29b, the spring portion 29c, and the facing portions 29d and 29e, and the spring portion 29c meshes with the gears 22 and 24. Function as biasing means for biasing each other in the radial direction toward each other to elastically mesh with each other, and the facing portions 29d, 29e serve as restriction means for restricting the movement of the gears 22, 24 in the tooth width direction. Both gears 2 to function
It is possible to prevent rattling (backlash) at the meshing portions of the gears 2 and 24 and suppress the generation of rattling noise, and to prevent the gears 22 and 24 from getting out of mesh with each other. The meshing of the gears 22 and 24 can be guaranteed. Further, both the functions of the urging means and the restricting means described above can be exerted by the single locking member 29, the generation of rattling noise can be suppressed with a simple and inexpensive structure, and each gear 22, 24 engagements can be guaranteed.

FIGS. 15 and 16 show a first modification of the locking member 29 shown in FIGS. 13 and 14, and the first modification is shown.
The locking member 129 of the modified example is formed by processing a wire rod, and is a part of the mounting holes 22a and 24a of the gears 22 and 24 (with the rotation axis L2 and L4 of the gears 22 and 24 as the center). Spirally-cylindrical engaging portions 129a and 129b that are elastically engaged with the gears 22 and 24 to allow the rotation of both gears 22 and 24, and the gears 22 and 24 as meshing portions. Spiral springs 129c and 129d that urge each other in a radial direction toward each other and elastically mesh with each other, and these springs 1
29 c and 129 d between the gears 22 and 24 and an opposed portion 129 e that restricts the movement of the gears 22 and 24 to the outside (tooth width direction), and the gears 2 are provided at the ends of the engagement portions 129 a and 129 b.
Substantially semicircular locking portions 129a1 and 129b1 that are slidably locked to the side surfaces of 2, 24 are formed. The intermediate portion of the facing portion 129e may be formed in a chevron shape as shown by an imaginary line, and this portion may also be implemented as a spring portion. In this locking member 129, the same function as that of the locking member 29 shown in FIGS. 13 and 14 is obtained, and since the engaging portions 129a, 129b are formed in the spiral cylindrical shape, the respective gears 22, 24 mounting holes 22a,
Even if the manufacturing precision of 24a is set low, it is possible to follow.

17 and 18 show a second modification of the locking member 29 shown in FIGS. 13 and 14, and this second
The locking member 229 of the modified example is formed by processing a wire material having a circular cross section, and is provided with the mounting holes 22 of the gears 22 and 24.
a, a part of 24a (rotation axis L2 of each gear 22, 24)
Engagement portion 2 which is formed in an arc shape centered on L4 and elastically engages with a portion) to allow rotation of both gears 22 and 24.
29a, 229b, a mountain-shaped spring portion 229c that biases the gears 22, 24 in the radial direction toward each other and elastically meshes them, and between the spring portion 229c and the engaging portions 229a, 229b. The facing portions 229d and 229e for restricting the movement of the gears 22 and 24 to the outside (tooth width direction)
Locking portions 129a1 and 129b1 that slidably lock to the side surfaces of the gears 22 and 24 are formed at the ends of the engaging portions 229a and 229b, respectively. In this locking member 229, a function equivalent to that of the locking member 29 shown in FIGS. 13 and 14 is obtained, and since each part is easily processed, it can be implemented at low cost.

FIGS. 19 and 20 show a third modification of the locking member 29 shown in FIGS. 13 and 14, and the third modification is shown.
The locking member 329 of the modified example is formed by processing an iron plate and press-fitting and caulking a pair of pins on the iron plate.
Part of the mounting holes 22a, 24a of the gears 2, 24 (each gear 22,
Engagement portions (pins) 329a and 329b that are elastically engaged with an arc shape centering around the rotation axis lines L2 and L4 of 24 and allow rotation of both gears 22 and 24. , A chevron-shaped spring portion 329c that elastically biases the gears 22 and 24 toward the meshing portion in a radial direction to mesh with each other.
And engaging portions 329d and 329e between the spring portion 329c and the engaging portions 329a and 329b for restricting movement of the gears 22 and 24 to the outside (tooth width direction). An annular locking portion (annular collar) 32 slidably locked to the side surfaces of the gears 22 and 24 at the ends of 329a and 329b.
9a1 and 329b1 are formed. This locking member 3
29, the locking member 2 shown in FIG. 13 and FIG.
Since the function equivalent to that of No. 9 is obtained, and it is composed of an iron plate and a pin, the requirements of each part in each part (for example, the cylindrical accuracy in the engaging part that allows the rotation of both gears 22 and 24, or in the facing part) It is easy to tune according to the pressure receiving area that receives a couple of force and the rigidity).

[Brief description of drawings]

FIG. 1 is a side view showing a first embodiment of a constant velocity universal joint according to the present invention.

2 is a partially cutaway side view of the constant velocity universal joint shown in FIG.

FIG. 3 is a side view of the holder and the gear shown in FIGS. 1 and 2.

FIG. 4 is a partially cutaway plan view of the holder and the gear shown in FIGS. 1 and 2.

5 is a side view of the input shaft and the output shaft shown in FIGS. 1 and 2. FIG.

6 is a partially cutaway plan view of the input shaft and the output shaft shown in FIGS. 1 and 2. FIG.

FIG. 7 is a side view showing a second embodiment of the constant velocity universal joint according to the present invention.

FIG. 8 is a side view showing a third embodiment of the constant velocity universal joint according to the present invention.

FIG. 9 is a side view showing a fourth embodiment of the constant velocity universal joint according to the present invention.

FIG. 10 is a side view showing a fifth embodiment of the constant velocity universal joint according to the present invention.

FIG. 11 is a side view showing another embodiment of the interlocking mechanism in the constant velocity universal joint according to the present invention.

12 is a side view of the gear shown in FIG. 11. FIG.

FIG. 13 is a front view of the locking member alone shown in FIG.

FIG. 14 is a bottom view of the locking member alone shown in FIG. 11.

FIG. 15 is a front view showing a first modified example of the locking member alone.

16 is a bottom view of the locking member alone shown in FIG.

FIG. 17 is a front view showing a second modified example of the locking member alone.

FIG. 18 is a bottom view of the locking member alone shown in FIG.

FIG. 19 is a front view showing a third modified example of the locking member alone.

FIG. 20 is a bottom view of the locking member alone shown in FIG.

[Explanation of symbols]

11 ... Intermediate shaft, 12, 14 ... Cross joint, 13 ... Input shaft,
15 ... Output shaft, 20 ... Interlocking mechanism, 21 ... Input side holder,
22 ... Input side gear, 23 ... Output side holder, 24 ... Output side gear, 25, 26 ... Holding plate, 27 ... Tension coil spring, 28 ... Torsion spring, 29 ... Locking member, 29a, 29b ... Engaging portion, 29c ... Spring part, 29
d, 29e ... Opposing portion, L1 ... Intermediate shaft axis, L2 ... Input rotation axis, L3 ... Input shaft axis, L4 ... Output rotation axis, L5 ... Output shaft axis, O1 ... Input cross Joint center of joint, O2 ... Joint center of cross joint on output shaft side, θi ... Joint angle on input shaft side, θo ... Joint angle on output shaft side, S ... Reference plane, A1-A5 ... Constant velocity universal joint.

Claims (5)

[Claims] 1. An input shaft at each cross joint having cross joints at both ends of the intermediate shaft in plane symmetry with respect to a reference plane that includes a midpoint between the two cross joints and is orthogonal to the axis of the intermediate shaft. A constant velocity universal joint that connects the input shaft and the output shaft so that torque can be transmitted, and the input shaft and the output shaft are rotatably assembled to the outer circumferences of the respective shaft ends. A constant velocity universal joint, which is arranged outside the intermediate shaft, allows rotation about each axis, and is connected by an interlocking mechanism capable of changing each joint angle with the intermediate shaft in a symmetrical relationship. 2. An input side holder, which is rotatably assembled to the outer periphery of the shaft end of the input shaft to allow rotation of the input shaft around its axis, and a member which is orthogonal to the axis of the input shaft. An input gear that is integrally formed in the input holder and is formed in an arc shape centered on an input rotation axis that passes through the joint center of the cruciform joint on the input shaft side, and an outer circumference of the shaft end of the output shaft. An output side holder that is rotatably mounted on the output shaft and allows rotation around the axis of the output shaft; and a holder that is orthogonal to the axis of the output shaft and that passes through the joint center of the cross joint on the output shaft side and the input side rotation. An output formed in an arc shape centering on an output side rotation axis parallel to the moving axis and integrally provided on the output side holder and meshing with the input side gear at an intermediate portion between the two cross joints. Claims characterized in that it is provided with a side gear The constant velocity universal joint according to Item 1. 3. The constant velocity universal joint according to claim 2, further comprising an urging means for urging the input side gear and the output side gear toward each other in a radial direction toward the meshing portion to elastically mesh with each other. A constant velocity universal joint characterized by being provided. 4. The constant velocity universal joint according to claim 2, further comprising a regulating means for regulating the movement of the input side gear and the output side gear in the tooth width direction. . 5. The constant velocity universal joint according to claim 2, wherein an engaging portion that engages with the input side gear and the output side gear to allow rotation of the both gears, and the input side gear. A spring portion that biases the output side gear toward the meshing portion in a radial direction to elastically mesh with each other, and a facing portion that restricts the movement of the input side gear and the output side gear in the tooth width direction. A constant velocity universal joint, characterized in that the input side gear and the output side gear are connected by a locking member having.