JPH01206148A - Speed change joint - Google Patents

Abstract

PURPOSE:To prevent local abrasion and simplify a structure by rotatably holding a first rolling element which is slidably brought into contact with first and second guide faces and a second rolling element slidingly brought into contact with the first and a third guide faces, on a retainer. CONSTITUTION:By moving an operating member 4 in the axial direction, the relative position in the axial direction of second and third guide faces 12, 18 to a first guide face 7 is changed and, in accordance with this, the sliding contact positions of the first and second rolling bodies 5, 6 with the guide faces 7, 12, 18 are changed. The way of transmitting revolving components of the rolling elements 5, 6 between an input shaft 1 and an output shaft 2 is changed to achieve speed change. Further, since the sliding contact positions between the first and second rolling elements 5, 6 and guide faces 7, 12, 18 are changed, the generation of local abrasion can be avoided. Also, since it is not necessary to energize the rolling elements with springs as before, there is no fear of deterioration enabling the structure to be simplified as much.

Description

[Detailed description of the invention] A1 Purpose of the invention (1) Industrial application fields The present invention relates to a speed change joint.

(2) Conventional technology Conventionally, a rolling element such as a steel ball interposed between an input side and an output side is rotated and revolved around its own axis by the rotational force from the input side, and the revolution component of the rolling element is There is a speed change joint that transmits power to the output side.

(3) Problems to be Solved by the Invention However, in the conventional device described above, since the rolling elements are always in sliding contact at one point, there is a risk of local wear. Further, in order to maintain the sliding state of the rolling elements, the rolling elements are urged by a spring such as a disc spring, and there is a risk that the springs deteriorate over time.

The present invention has been made in view of the above circumstances, and it is an object of the present invention to provide a speed change joint that prevents local wear and eliminates the need to bias rolling elements with springs or the like, which may be subject to deterioration. purpose.

B0 Configuration of the Invention (1) Means for Solving the Problems According to the present invention, the input shaft has a first recessed in an arc shape on the outer surface of the input shaft.
A transmission member having a tapered second guide surface coaxially surrounding the first guide surface is prevented from relative rotation on the output shaft, which is provided with a guide surface perforated along the entire circumference and coaxially arranged with the input shaft. The transmission member is connected to allow relative movement in the axial direction with the input shaft and the output shaft, and is allowed to move relative to the input shaft and the output shaft in the axial direction, and is prevented from angular displacement around the axis while maintaining a constant relative position in the axial direction to the transmission member. The operation member to be connected is provided with a tapered third guide surface that faces the second guide surface and coaxially surrounds the first guide surface, and the retainer is rotatable relative to the input shaft and the output shaft. , a plurality of spherical first rolling elements in sliding contact with the first guide surface and the second guide surface, and spherical second rolling elements in sliding contact with the first guide surface and the third guide surface, spaced at equal intervals in the circumferential direction. They are rotatably held while slidingly touching each other at certain points.

(2) Effect According to the above configuration, by moving the operating member in the axial direction, the relative axial positions of the second and third guide surfaces with respect to the first guide surface change, and the first and second guide surfaces change accordingly. The sliding position of the rolling element on each guide surface changes, and the way in which the revolution component of the rolling element is transmitted between the input shaft and the output shaft changes, thereby achieving speed change. Furthermore, since the sliding contact positions between the first and second rolling elements and each guide surface change, local wear is avoided, and since it is not necessary to bias the rolling elements with a spring, there is no risk of deterioration.

(3) Embodiment An embodiment of the present invention will be explained below with reference to the drawings. First, in FIG. 1, this transmission joint has an input shaft 1,
An output shaft 2 disposed coaxially with the input shaft 1, a transmission member 3 connected to the output shaft 2 while allowing relative movement in the axial direction but preventing relative rotation around the axis, and the transmission member 3. The operating member 4 coaxially surrounds the input shaft 11, the output shaft 2, and the transmission member 3 with a constant relative position in the axial direction, and the input shaft 1 and the transmission member are held by a retainer 19 at a plurality of positions equally spaced in the circumferential direction. 3 and spherical first and second rolling elements 5.6 interposed between the input shaft 1 and the operating member 4, respectively.

On the outer surface of the input shaft l, a first guide surface 7 is provided over the entire circumference, with a cross-sectional shape including the axis line being arcuate. Further, the output shaft 2 is disposed coaxially opposite to the end surface of the input shaft 1, and is connected to both wheels 1. 2 are connected via two thrust bearings 8 and 9. That is, the output shaft 2 is formed into a bottomed cylindrical shape with the closed end facing the input shaft 1 side.
An insertion hole 20 is provided at the closed end. Further, the thrust bearing 8 is interposed between the closed end of the output shaft 2 and the end surface of the input shaft l, and is inserted into the insertion hole 20 and screwed into the end of the input shaft l. A thrust bearing 9 is interposed between the output shaft 2 and the closed end.

As a result, the input shaft 1 and the output shaft 2 are connected to each other while being allowed to rotate relative to each other while being prevented from moving relative to each other in the axial direction.

The transmission member 3 includes a large-diameter cylindrical portion 3a that coaxially surrounds the end of the input shaft l, and a small-diameter cylindrical portion 3 that coaxially surrounds the end of the output shaft 2.
b are coaxially connected via a stepped portion 3c, and the inner surface of the small diameter cylindrical portion 3b and the outer surface of the output shaft 2 are coupled via a spline 11. Therefore, the transmission member 3 can move relative to the output shaft 2 in the axial direction and
Relative angular displacement with respect to is prevented. Furthermore, a tapered second guide surface 12 that coaxially surrounds the first guide surface 7 is provided on the end surface of the large diameter cylindrical portion 3a of the transmission member 3.

The operating member 4 is movable in the axial direction and prevented from rotating around the axis, and is formed into a cylindrical shape that coaxially surrounds the input shaft 1, the output shaft 2, and the transmission member 3.

The end caps of two examples of the output shafts of the operating member 4 are integrally provided with a flange portion 4a projecting radially inward, and the flange portion 4a
An annular sealing member 1 is provided between the inner edge of the output shaft 2 and the outer surface of the output shaft 2.
3 is interposed. Further, a thrust bearing 14 is interposed between the collar portion 4a and the stepped portion 3C of the transmission member 3.

A cylindrical member 15 coaxially surrounding the input shaft 1 is screwed onto the inner surface of the input shaft 1 side end of the operating member 4, and the cylindrical member 15 is substantially integrated with the operating member 4.

Further, an annular seal member 16 is interposed between the cylindrical member 15 and the operating member 4, and an annular seal member 17 is interposed between the cylindrical member 15 and the input shaft 1. Moreover, the inner end surface of the cylindrical member 15 is provided with a tapered third guide surface 1 coaxially surrounding the first guide surface 7 and facing the second guide surface 12.
8 is provided.

Referring also to FIG. 2, the first and second rolling elements 5, 6
is rotatably held by a retainer 19 that can freely rotate around the same axis as the input shaft 1. The retainer 19
A holding part 19b is provided at the end of a cylindrical part 19a coaxially arranged between the transmission member 3 and the operating member 4,
The first rolling element 5 and the second rolling element 6 are rotatably held in the holding portion 19b in sliding contact with each other at a plurality of circumferential positions, for example, five positions. Furthermore, the first rolling element 5 is in sliding contact with the first guide surface 7 and the second guide surface 12, and the second rolling element 6 is in sliding contact with the first guide surface 7 and the third guide surface 18.

In this way, the first and second rolling elements 5 and 6 are interposed between the transmission member 3 and the cylindrical member 15, that is, the operating member 4, and the thrust bearing 14 is interposed, so that the operating member 4 The transmission member 3 also moves in accordance with the axial movement, and the axial distance between the second guide surface 12 and the third guide surface 18 is always kept constant.

Incidentally, the space surrounded by the operating member 4, the cylindrical member 15, the input shaft 1, and the output shaft 2 is filled with lubricating oil, but the filled oil leaks from the thrust bearing 9 onto the inner surface of the intermediate portion of the output shaft 2. A disc-shaped cover plate 21 for preventing this is fixed to the inner surface of the output shaft 2 with a seal member 22 interposed therebetween.

Next, to explain the operation of this embodiment, let us first assume that the first and second rolling elements 5.6 are brought into a posture in which their rotation axes C are parallel to the input shaft 1 by operating the operating member 4 in the axial direction. . At this time, when rotational force is input from the input shaft 1, the third guide surface 18 is in a fixed state, so the second rolling element 6 rotates around the input shaft 1 according to the rotation of the first guide surface 7. Therefore, the retainer 19 also rotates around the axis. On the other hand, the first rolling element 6 rotates around the rotation axis C due to sliding contact with the first guide surface 7, but since the retainer 19 is rotating around the axis, it revolves around the axis of the input shaft 1. At this time, the rotation axes C of both rolling elements 5.6 are coaxial, and the sliding positions of the first rolling element 5 on the first and second guide surfaces 7.12 are set to PL, P2, and the first rolling element 5.
The position of sliding contact with the first and third guide surfaces 7, 18 is P3.
．． If P4 is the sliding contact position Pl from the axis of the input shaft 1.

The distance from the axis of the input shaft 1 to the sliding contact position P2. Since the distance to P4 is the same, the first
The rolling elements 5 slide on the second guide surface 12. As a result,
No rotational force is transmitted from the first rolling element 5 to the second guide surface 12, and the output shaft 2 remains stationary without rotating.

Next, assume that the operating member 4 is operated in the axial direction to tilt the rotation axis C with respect to the axis of the input shaft 1, as shown in FIG. In this state, the second rolling element 6 rotates and revolves around the rotation axis C as described above, and the first rolling element 5 also revolves while rotating around the rotation axis C. The sliding contact positions of the first rolling element 5 with the first and second guide surfaces 7.12 are PI' and P2', and the sliding contact positions of the first rolling element 5 with the first and third guide surfaces 7.18 are P3' and P4.
', the distance from the axis of the input shaft 1 to the sliding contact position P1' is greater than the distance to the sliding contact position P3', and the distance from the axis of the input shaft 1 to the sliding contact position P2' is the sliding contact position. It is larger than the distance to P4'. Therefore, while the rotational speed of the first rolling element 5 is faster than the rotational speed of the second rolling element 6, the rotational speed of the retainer 19, that is, the revolution speed is regulated by the second rolling element 6, so that the difference can be accommodated. The rotational force is transmitted from the first rolling element 5 to the second guide surface 12. Therefore, rotational force is transmitted to the output shaft 2.

The amount of rotational force transmitted to the output shaft 2 is determined by the inclination ratio of the rotation axes C of the first and second rolling elements 5 and 6 with respect to the axis of the input shaft 1. By operating the input shaft 1 to determine the inclination ratio,
It becomes possible to steplessly control the rotational force transmission ratio from to the output shaft 2, that is, the gear ratio.

Further, if the rotation direction of the output shaft 2 in the state shown in FIG. 3 is the positive direction, the rotation axis C of the first and second rolling elements 5°
It is also possible to rotate the output shaft 2 while changing the speed in the opposite direction by setting the inclination direction of the output shaft 2 to the direction opposite to that shown in FIG.

C0 Effects of the Invention As described above, according to the present invention, the first guide surface recessed in an arc shape is provided on the outer surface of the input shaft over the entire circumference, and the output shaft arranged coaxially with the input shaft has the following features: A transmission member having a tapered second guide surface coaxially surrounding the first guide surface is coupled to prevent relative rotation and allow relative axial movement, and is connected to the input shaft and the output shaft in an axially relative manner. The operating member, which is allowed to move and is prevented from angular displacement around the axis, and which is connected to the transmission member while maintaining a constant relative position in the axial direction, has a first guide surface that coaxially surrounds the first guide surface, facing the second guide surface. A retainer is provided with a tapered third guide surface that is rotatable relative to the input shaft and the output shaft, a spherical first rolling element that is in sliding contact with the first guide surface and the second guide surface, and a first guide. Since the spherical second rolling element that is in sliding contact with the surface and the third guide surface is rotatably held while slidingly contacting each other at multiple locations equidistantly spaced in the circumferential direction,
By operating the operating member in the axial direction and changing the postures of the first and second rolling elements, it is possible to steplessly adjust the gear ratio between the input shaft and the output shaft. Since there is no need for a spring or the like for biasing, there is no need to worry about deterioration, and since the sliding contact position of each rolling element with each guide surface changes, local wear can be prevented as much as possible.

[Brief explanation of the drawing]

The drawings show one embodiment of the present invention, and FIG. 1 is a longitudinal sectional view in a non-shifting state, FIG. 2 is a sectional view taken along the line ■-■ in FIG. 1, and FIG. 3 is a sectional view in a shifting state. FIG. 1 is a longitudinal cross-sectional view corresponding to FIG. 1... Input shaft, 2... Output shaft, 3... Transmission member,
4... Operating member, 5... First rolling element, 6... Second
Rolling element, 7...First guide surface, 12...Second guide surface, 18...Third guide surface, 19...Retainer Fig. 2

Claims (1)

[Claims] A first guide surface recessed in an arc shape is provided on the outer surface of the input shaft over the entire circumference, and a second tapered guide surface coaxially surrounding the first guide surface is provided on the output shaft coaxially with the input shaft. A transmission member having a guide surface is coupled so as to prevent relative rotation and allow relative axial movement, and is allowed to move relative to the input shaft and the output shaft in the axial direction and is prevented from angular displacement about the axis. The operation member, which is connected to the transmission member at a constant relative position in the axial direction, is provided with a tapered third guide surface that faces the second guide surface and coaxially surrounds the first guide surface. and a spherical first rolling element that is in sliding contact with the first guide surface and the second guide surface, and a spherical second rolling element that is in sliding contact with the first guide surface and the third guide surface, and a retainer that is rotatable relative to the output shaft. A speed change joint characterized in that a moving body is rotatably held while slidingly contacting each other at a plurality of locations equally spaced in the circumferential direction.