JP2009264509A - Shaft coupling and pulley having the same - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a shaft coupling and a pulley having the same, restraining machining cost. <P>SOLUTION: This shaft coupling has: a plurality of cylindrical rollers 60 arranged in a plurality in the peripheral direction of a clearance between a primary shaft 25 and a cylindrical part 50 and rollable in the axial direction by rollingly contacting with an outer peripheral surface of the primary shaft 25 and an inner peripheral surface of the cylindrical part 50; an inner shaft side plane 41 formed on the outer peripheral surface of the primary shaft 25 rollingly contacting with the respective cylindrical rollers 60, orthogonal to the radial direction of the primary shaft 25 and extending in the axial direction; and an outer shaft side plane 56 formed on the inner peripheral surface of the cylindrical part 50 rollingly contacting with the respective cylindrical rollers 60, opposed in parallel to the inner shaft side plane, orthogonal to the radial direction of the cylindrical part 50 and extending in the axial direction. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a shaft joint capable of regulating displacement in the circumferential direction and capable of displacement in the axial direction, and a pulley including the same.

  Conventionally, a spline shaft is known as a general shaft joint, and is used, for example, in a primary pulley of a belt-type continuously variable transmission (see, for example, Patent Document 1). The primary pulley is composed of a fixed sheave integrally formed on the outer periphery of the primary shaft and a movable sheave slidably mounted on the outer periphery of the primary shaft. A plurality of splines (teeth) are formed on the inner peripheral surface of the movable sheave, and a plurality of splines engaged with the plurality of splines of the movable sheave are formed on the outer peripheral surface of the primary shaft that slidably supports the movable sheave. Spline grooves are formed. Accordingly, the movable sheave is configured to be movable in the axial direction with respect to the primary shaft, but is configured to be immovable in the circumferential direction.

JP 2004-257468 A

  However, in a configuration such as a conventional primary pulley, processing must be performed with high accuracy so that there is no deviation in meshing between the plurality of spline teeth and the plurality of spline grooves. That is, when the meshing accuracy of the plurality of spline teeth and the plurality of spline grooves is poor, the phase (position) of each spline tooth and each spline groove is shifted, so the movable sheave is rotated in the circumferential direction with respect to the primary shaft. At this time, there is a possibility that the spline teeth and the spline groove are in contact with each other in the circumferential direction and some are not in contact with each other. In this case, a large load is applied to the spline teeth and spline grooves that contact in the circumferential direction. For this reason, in order to make the meshing accuracy of the plurality of spline teeth and the plurality of spline grooves accurate, it is necessary to perform high-accuracy processing, and it is difficult to suppress the processing cost.

  Further, in order to stably move the movable sheave in the axial direction with respect to the primary shaft, sliding contact surfaces that are in sliding contact with each other are formed on the outer peripheral surface of the primary shaft and the inner peripheral surface of the movable sheave. When the movable sheave moves in the axial direction with respect to the primary shaft, the sliding contact surface of the movable sheave moves while sliding on the sliding contact surface of the primary shaft. Therefore, each sliding contact surface is controlled to suppress energy loss due to friction. However, it was necessary to polish the surface. Thereby, although the movement of the movable sheave in the axial direction with respect to the primary shaft becomes smooth, it is difficult to suppress the processing cost because polishing must be performed.

  Then, this invention makes it a subject to provide the shaft coupling which can suppress processing cost, and a pulley provided with the same.

  The shaft joint of the present invention is a shaft joint that restricts the relative displacement in the circumferential direction between the inner shaft and the outer shaft and allows the relative displacement in the axial direction between the inner shaft and the outer shaft. A plurality of rotating bodies that are arranged in the circumferential direction of the gap between the inner shaft and that are in rolling contact with the outer peripheral surface of the inner shaft and the inner peripheral surface of the outer shaft to roll in the axial direction; Formed on the outer peripheral surface and formed on a plurality of inner shaft side planes extending in the axial direction of the inner shaft, and on the inner peripheral surface of the outer shaft to which each rotating body comes into rolling contact, facing the inner shaft side plane in parallel, And a plurality of outer shaft side planes extending in the axial direction of the shaft.

  In this case, each rotating body is preferably formed in a cylindrical shape whose axis is perpendicular to the axial direction of the inner shaft.

  Further, in this case, the plurality of rotating bodies are divided into a plurality of rotating body groups according to the plurality of inner shaft side planes and the plurality of outer shaft side planes, and the plurality of rotating bodies in each rotating body group. Are preferably arranged in parallel in the axial direction of the inner shaft.

  On the other hand, each rotating body is formed in a spherical shape, and the plurality of rotating bodies are arranged in a plurality of rotating body groups according to a plurality of inner-axis-side planes and a plurality of outer-axis-side planes, The plurality of rotating bodies in the rotating body group may be arranged in parallel in the circumferential direction of the inner shaft.

  In these cases, it is preferable to further include a rotating body holding member that is provided in a gap between the inner shaft and the outer shaft and holds the posture of each rotating body.

  In this case, it is preferable that the rotating body holding member is configured to be separable.

  In this case, it is preferable that a washer provided between the rotating bodies of each rotating body group is further provided.

  A pulley according to the present invention is arranged to face the fixed coupling, the inner shaft, a fixed sheave formed integrally with one end of the inner shaft, and the fixed sheave. And a movable sheave having an annular portion formed integrally.

  In this case, it is preferable that the movable sheave is further provided with a stopper that is disposed at the other end of the outer shaft and prevents deviation of each rotating body.

  The shaft joint and pulley according to the present invention have a plurality of rotating bodies arranged in the gap between the inner shaft and the outer shaft, and the outer peripheral surface of the inner shaft with which the rotating body is in rolling contact is formed on the inner shaft side plane. The inner peripheral surface of the outer shaft with which the roller contacts is formed on the outer shaft side plane, and the inner shaft side plane and the outer shaft side plane can be made parallel to each other. For this reason, when the outer shaft tends to be displaced in the circumferential direction with respect to the inner shaft, the parallel state between the inner shaft side plane and the outer shaft side plane tends to collapse, but there is a gap between the inner shaft side plane and the outer shaft side plane. Since the rotating body interposed between the two is not configured to roll in the circumferential direction, it tends to maintain a parallel state between the inner shaft side plane and the outer shaft side plane. Thereby, the displacement to the circumferential direction of the outer shaft with respect to an inner shaft can be controlled. For this reason, it is not necessary to provide spline teeth and spline grooves on the inner shaft and the outer shaft, and it is only necessary to form planes on the inner shaft and the outer shaft, so that the processing cost can be suppressed. Also, by arranging a plurality of rotating bodies in the gap between the inner shaft and the outer shaft, the axial direction of the inner shaft and the outer shaft can be made coaxial. In other words, since the inner shaft can be centered with respect to the outer shaft, energy loss due to sliding resistance of the sliding contact surface of the outer shaft and the sliding contact surface of the inner shaft can be suppressed, and each sliding contact surface is polished. There is no need for processing, and the processing cost can be reduced.

  Hereinafter, a pulley having a shaft joint according to the present invention will be described with reference to the accompanying drawings. Note that the present invention is not limited to the embodiments.

  Here, FIG. 1 is a schematic configuration diagram illustrating a vehicle drive system to which a belt type continuously variable transmission having a primary pulley according to the first embodiment is applied, and FIG. 2 illustrates the primary pulley according to the first embodiment. It is an external perspective view. FIG. 3 is an exploded external perspective view of the primary pulley according to the first embodiment, and FIG. 4 is a half sectional view in the radial direction of the primary pulley according to the first embodiment. FIG. 5 is a cross-sectional view of the primary pulley according to the first embodiment in the axial direction.

  First, a vehicle drive system 1 will be described with reference to FIG. A vehicle drive system 1 includes an engine 5 serving as a drive source, a torque converter 6 coupled to the engine 5, a forward / reverse switching mechanism 7 coupled to the torque converter 6, and a belt coupled to the forward / reverse switching mechanism 7. A continuously variable transmission 8 is provided. A reduction gear 9 is connected to the belt-type continuously variable transmission 8, a differential device 10 is connected to the reduction gear 9, and a drive wheel 11 is connected to the differential gear 10.

  For example, a gasoline engine or a diesel engine is used as the engine 5, and the piston reciprocates in the central axis direction of the cylinder formed in a cylindrical shape, and the crankshaft 15 converts the reciprocating motion of the piston into a rotational motion. Outputs driving force.

  The torque converter 6 is a kind of fluid clutch, and transmits the driving force output from the engine 5 to the forward / reverse switching mechanism 7 via hydraulic oil. The torque converter 6 has a lockup mechanism, for example, and increases the output torque from the engine 5 or transmits it to the forward / reverse switching mechanism 7 with the output torque as it is.

  The belt-type continuously variable transmission 8 changes the rotational speed of the driving force input from the forward / reverse switching mechanism 7 to a desired rotational speed according to the driving state of the vehicle and outputs it. The detailed description of the belt type continuously variable transmission 8 will be described later.

  The speed reducer 9 reduces the rotational speed of the driving force input from the belt-type continuously variable transmission 8 and transmits the driving force to the differential device 10. The differential device 10 turns when the vehicle turns. The speed difference between the driving wheel 11 on the center side, that is, the inner driving wheel 11 and the outer driving wheel 11 is absorbed.

  Therefore, when the engine 5 is driven in the vehicle drive system 1, the driving force output from the engine 5 is transmitted to the torque converter 6 via the crankshaft 15. The driving force obtained by amplifying the output torque by the torque converter 6 is transmitted to the forward / reverse switching mechanism 7 and is changed to a desired rotation direction by the forward / backward switching mechanism 7. The driving force in the desired rotational direction is input to the belt-type continuously variable transmission 8, and the rotational speed of the input driving force is changed according to a predetermined gear ratio of the belt-type continuously variable transmission 8. The The driving force whose rotational speed has been changed by the belt-type continuously variable transmission 8 is input to the speed reducer 9, and the input driving force is decelerated by the speed reducer 9 and then output to the differential device 10. . Then, the differential device 10 transmits the input driving force to the driving wheels 11, so that the driving wheels 11 rotate, and thereby the vehicle travels.

  Next, the belt type continuously variable transmission 8 will be described. The belt type continuously variable transmission 8 includes a primary pulley 20 connected to the output shaft of the forward / reverse switching mechanism 7, a secondary pulley 21 provided opposite to the primary pulley 20, and the primary pulley 20 and the secondary pulley 21. A belt 22 is provided.

  The primary pulley 20 is slidably attached to a primary shaft 25 (inner shaft) connected to the output shaft of the forward / reverse switching mechanism 7, a primary fixed sheave 26 fixed to the primary shaft 25, and the primary shaft 25. And a primary movable sheave 27. The primary fixed sheave 26 and the primary movable sheave 27 are opposed to each other, and a substantially V-shaped primary groove V1 is formed therebetween. The primary movable sheave 27 is movable in the axial direction of the primary shaft 25 with respect to the primary fixed sheave 26, and the belt-type continuously variable transmission 8 moves the primary movable sheave 27 in the axial direction of the primary shaft 25. Thus, there is a primary hydraulic actuator 28 for moving the primary movable sheave 27 and the primary fixed sheave 26 closer to and away from each other.

  Similarly, the secondary pulley 21 also includes a secondary shaft 30 provided in parallel with the primary shaft 25, a secondary fixed sheave 31 fixed to the secondary shaft 30, and a secondary movable sheave 32 slidably mounted on the secondary shaft 30. And is constituted by. The secondary fixed sheave 31 and the secondary movable sheave 32 are opposed to each other, and a substantially V-shaped secondary groove V2 is formed therebetween. The secondary movable sheave 32 is movable in the axial direction of the secondary shaft 30 with respect to the secondary fixed sheave 31, and the belt-type continuously variable transmission 8 moves the secondary movable sheave 32 in the axial direction of the secondary shaft 30. The secondary hydraulic sheave 32 and the secondary fixed sheave 31 are moved to approach and separate from each other, and the secondary hydraulic actuator 33 is provided.

  The belt 22 is a metal endless belt, and is wound around the primary groove V1 and the secondary groove V2. The primary hydraulic actuator 28 and the secondary hydraulic actuator 33 change the groove width of the primary pulley 20 and the secondary pulley 21 as appropriate, thereby changing the winding radius of the belt 22. As a result, the belt type continuously variable transmission 8. Is set to a desired gear ratio.

  Here, with reference to FIG. 2 thru | or FIG. 5, the primary pulley 20 which concerns on Example 1 is demonstrated concretely. As described above, the primary pulley 20 has the primary shaft 25, the primary fixed sheave 26, and the primary movable sheave 27. The primary shaft 25 and the primary movable sheave 27 are connected by the shaft joint 35 of the present invention. Has been. Here, the shaft joint 35 that connects the primary shaft 25 and the primary movable sheave 27 will be described in detail.

  The primary shaft 25 is formed in a columnar shape, and a plurality of inner shaft side planes 41 (for example, three in the first embodiment) are formed on the outer peripheral surface thereof. Each inner shaft side plane 41 is formed to be a plane orthogonal to the center line H with the radial direction of the primary shaft 25 as the center line H, and is formed to extend in the axial direction (FIG. 3). And FIG. 5). That is, each inner shaft side plane 41 is flat in the tangential direction and the axial direction orthogonal to the radial direction of the primary shaft 25. The three inner shaft planes 41 are formed at equal intervals in the circumferential direction of the primary shaft 25, that is, with a phase shift of 120 degrees, and each inner shaft plane 41 is on the output shaft side of the primary shaft 25. It is formed from the end portion 25 b to the central portion 25 c of the primary shaft 25.

  The primary fixed sheave 26 is fixed so as to be integrated with the outer peripheral surface of the input shaft side end portion 25 a of the primary shaft 25 at a predetermined distance from each inner shaft side plane 41. For this reason, the outer peripheral surface of the primary shaft 25 between the primary fixed sheave 26 and each inner shaft side plane 41 is a fixed-side sliding main surface 42 with which the inner peripheral surface of the primary movable sheave 27 is in sliding contact.

  The primary movable sheave 27 includes a cylindrical portion 50 (outer shaft) provided around the primary shaft 25 and an annular portion 51 provided at the input shaft side end portion 50 a of the cylindrical portion 50 so as to face the primary fixed sheave 26. And. And the axial center of the cylindrical part 50 is arrange | positioned so that it may become coaxial with the axial center of the primary shaft 25, and the cyclic | annular part 51 is made to protrude in the radial direction outer side from the input-shaft side edge part 50a of the cylindrical part 50, and is formed. Yes. Further, a stepped through hole 53 is formed in the axial center of the cylindrical portion 50, and the through hole 53 is formed on the large diameter side through hole 53a formed on the output shaft side and on the input shaft side. It is comprised by the small diameter side through-hole 53b (refer FIG. 4). The inner peripheral surface of the small diameter side through hole 53b is a movable sliding main surface 55 that is in sliding contact with the fixed sliding main surface 42 of the primary shaft 25. On the other hand, on the inner peripheral surface of the large diameter side through hole 53a, a plurality of outer shaft side planes 56 (for example, three in the first embodiment) facing each inner shaft side plane 41 formed in the primary shaft 25 in parallel. Is formed. Each outer shaft side plane 56 is formed to be a plane orthogonal to the center line H with the radial direction of the cylindrical portion 50 as the center line H (see FIG. 5), and is formed to extend in the axial direction. ing. For this reason, the cross section of the large-diameter side through hole 53a is formed in a rounded triangular shape.

  Between each inner shaft side plane 41 of the primary shaft 25 and each outer shaft side plane 56 of the large diameter side through hole 53a, a plurality of rotating bodies (for example, 15 in the first embodiment) are provided. Each rotating body is a cylindrical roller 60 formed in a cylindrical shape. The plurality of cylindrical rollers 60 are divided into three cylindrical roller groups 61 according to the three inner-axis-side planes 41 and the three outer-axis-side planes 56, and the three cylindrical roller groups 61 are arranged on the inner-axis side. They are respectively disposed in the gaps between the plane 41 and the outer shaft side planes 56. Each cylindrical roller group 61 is composed of five cylindrical rollers 60 and is arranged in parallel in the axial direction.

  Each cylindrical roller 60 has an axial direction orthogonal to the axial direction of the primary shaft 25, and a distance L between the inner shaft side plane 41 and the outer shaft side plane 56 whose diameters are parallel to each other. The same length or slightly larger diameter is formed. Each cylindrical roller 60 is press-fitted between the inner shaft side plane 41 and the outer shaft side plane 56. Thereby, as shown in FIG. 5, each cylindrical roller 60 is in rolling contact with each inner shaft side plane 41 of the primary shaft 25, and on each outer shaft side plane 56 of the large diameter side through hole 53 a of the primary movable sheave 27. It comes into rolling contact and can roll in the axial direction. That is, the shaft joint 35 according to the present invention includes a plurality of cylindrical rollers 60, a plurality of inner shaft side planes 41, and a plurality of outer shaft side planes 56.

  At this time, an annular stopper 63 protruding radially inward is disposed at the output shaft side end portion 50 b of the cylindrical portion 50 of the primary movable sheave 27. The stopper 63 prevents each cylindrical roller 60 from deviating from the gap between the primary shaft 25 and the cylindrical portion 50 when the primary movable sheave 27 moves in the axial direction toward the primary fixed sheave 26. Is for.

  Therefore, when the primary movable sheave 27 attempts to rotate relative to the primary shaft 25, each cylindrical roller 60 is press-fitted between each inner shaft side plane 41 and each outer shaft side plane 56. Therefore, the parallel state of each inner shaft side plane 41 and each outer shaft side plane 56 is maintained. For this reason, the rotation of the primary movable sheave 27 with respect to the primary shaft 25 is locked by each cylindrical roller 60. Accordingly, the primary movable sheave 27 is configured so as not to be displaced in the circumferential direction.

  On the other hand, when the primary movable sheave 27 is displaced relative to the primary shaft 25 in the axial direction, the primary movable sheave 27 has a movable side sliding main surface 55 that is an inner peripheral surface of the small diameter side through hole 53b. The cylindrical roller 60 rolls in the axial direction while sliding on the fixed sliding main surface 42 which is the outer peripheral surface of the primary shaft 25. Thus, the primary movable sheave 27 is configured to be axially displaceable by the cylindrical rollers 60 with the fixed-side sliding main surface 42 as a guide.

  According to the above configuration, it is not necessary to provide spline teeth on the primary movable sheave 27 and it is not necessary to form spline grooves on the primary shaft 25. That is, the inner shaft planes 41 may be formed on the outer peripheral surface of the primary shaft 25, and the outer shaft planes 56 may be formed on the inner peripheral surface of the cylindrical portion 50 of the primary movable sheave 27. For this reason, the shaft joint 35 in which the primary movable sheave 27 can be displaced in the axial direction but cannot be displaced in the circumferential direction with respect to the primary shaft 25 can be configured by simple processing. Further, as shown in FIG. 5, since the primary movable sheave 27 is disposed with respect to the primary shaft 25 via the respective cylindrical rollers 60, the axis of the primary movable sheave 27 with respect to the axis of the primary shaft 25. The heart can be coaxial. That is, since the primary shaft 25 can be centered with respect to the primary movable sheave 27, energy loss due to sliding resistance between the fixed sliding main surface 42 and the movable sliding main surface 55 can be suppressed. Since it is not necessary to polish the fixed-side sliding main surface 42 and the movable-side sliding main surface 55, the processing cost can be suppressed.

  Next, the primary pulley 70 according to the second embodiment will be described with reference to FIGS. 6 and 7. Only different parts will be described to avoid redundant description. 6 is an exploded perspective view of the primary pulley according to the second embodiment, and FIG. 7 is an external perspective view of a roller holding member. In the primary pulley 70 according to the second embodiment, the posture of each cylindrical roller 60 is set in the gap between the outer peripheral surface of the primary shaft 25 of the primary pulley 20 according to the first embodiment and the inner peripheral surface of the cylindrical portion 50 of the primary movable sheave 27. The roller holding member 71 (rotary body holding member) to hold is interposed.

  Specifically, the roller holding member 71 is formed in a cylindrical shape, and 15 roller accommodating portions 72 capable of accommodating 15 cylindrical rollers 60 are formed through the peripheral surface thereof. The fifteen roller accommodating parts 72 are divided into three roller accommodating part groups 73 according to the three inner shaft side planes 41 and the three outer axis side planes 56, and the three roller accommodating part groups 73 are: It is formed at equal intervals in the circumferential direction of the roller holding member 71, that is, by shifting the phase by 120 degrees. Each roller accommodating portion group 73 is composed of five roller accommodating portions 72 and is arranged in parallel in the axial direction. Each roller accommodating portion 72 is configured to have a size that can accommodate each cylindrical roller 60, and the diameter of each cylindrical roller 60 and the length of each roller accommodating portion 72 in the axial direction so that each cylindrical roller 60 does not swing. Are almost identical.

  Therefore, when the primary movable sheave 27 is displaced relative to the primary shaft 25 in the axial direction, each cylindrical roller 60 moves to the inner shaft of the primary shaft 25 as the primary movable sheave 27 moves in the axial direction. The side plane 41 and each outer shaft side plane 56 of the cylindrical portion 50 roll. At this time, each cylindrical roller 60 rolls in a state orthogonal to the axial direction of the primary shaft 25 without being shaken because the posture is held by the roller holding member 71. For this reason, since the inner shaft side plane 41 and the outer shaft side plane 56 are in uniform contact with the outer peripheral surface of each cylindrical roller 60 in the axial direction of each cylindrical roller 60, the load applied to each cylindrical roller 60 is equalized. It can be. Thereby, since the abnormal wear of each cylindrical roller 60 due to the bias of the load can be suppressed, the durability of the primary pulley 70 can be improved.

  In the second embodiment, the roller holding member 71 is composed of one member. However, as shown in FIG. 8, the roller holding member 71 may be composed of a plurality of divided holding members 75 and can be divided. . Specifically, FIG. 8 is a front view of the roller holding member in the axial direction, and the roller holding member 71 includes a plurality of cylindrical rollers 61 arranged at equal intervals in the circumferential direction. The divided holding members 75 are formed in a circular arc shape in cross section. Accordingly, it is not necessary to dispose the roller holding member 71 together with each cylindrical roller 60, and each divided holding member 75 can be disposed after the respective cylindrical rollers 60 are disposed. 71 can be provided.

  Next, the primary pulley 80 according to the third embodiment will be described with reference to FIG. In this case as well, only different parts will be described to avoid redundant description. FIG. 9 is an external perspective view in which the primary pulley according to the third embodiment is disassembled. The primary pulley 80 according to the third embodiment has a configuration in which a plurality of flat washers 81 are provided instead of the roller holding member 71 provided in the primary pulley 70 according to the second embodiment.

  Specifically, a plurality (for example, four in the third embodiment) of flat washers 81 are interposed between the five cylindrical rollers 60 in the three cylindrical roller groups 61. That is, one flat washer 81 is interposed between the first cylindrical roller 60 and the second cylindrical roller 60 from the input shaft side of each cylindrical roller group 61, and similarly, the second and third Flat washers 81 are interposed between the eyes, between the third and fourth, and between the fourth and fifth. At this time, each flat washer 81 is formed so that the outer periphery thereof is smaller in diameter than the inner periphery diameter of the large-diameter side through hole 53a of the primary movable sheave 27, and the inner periphery thereof is larger than the outer diameter of the primary shaft 25. It has a large diameter.

  According to this configuration, since each cylindrical roller 60 is held between the flat washers 81, each cylindrical roller 60 does not run out. Thereby, since the shaft runout can be prevented by using the flat washer 81 which is cheaper than the roller holding member 71 of the second embodiment, the manufacturing cost of the primary pulley 80 can be suppressed.

  Here, a modification of the primary pulley 90 according to the third embodiment will be described with reference to FIGS. 10 and 11. In this case as well, only different parts will be described to avoid redundant description. FIG. 10 is an external perspective view in which a primary pulley according to a modification of the third embodiment is disassembled, and FIG. 11 is an external perspective view of a flat washer with a claw used for the primary pulley according to the modification of the third embodiment. . A primary pulley 90 according to a modification of the third embodiment is obtained by adding a claw 91 to the flat washer 81 of the third embodiment.

  Specifically, each flat washer 81 is formed with three pairs of claw portions 91 protruding in the axial direction at predetermined intervals in the circumferential direction. The pair of claw portions 91 has substantially the same length as the axial length of each cylindrical roller 60. By disposing each cylindrical roller 60 between the pair of claw portions 91, The movement of each cylindrical roller 60 in the circumferential direction is restricted.

  According to this configuration, each cylindrical roller 60 is held between the pair of claw portions 91 of each flat washer 81, so that the movement of each cylindrical roller 60 in the circumferential direction can be restricted. Thereby, since the attitude | position of each cylindrical roller 60 can be controlled in an axial direction and the circumferential direction, compared with the flat washer 81 of Example 3, the attitude | position of each cylindrical roller 60 can be hold | maintained more firmly. it can.

  In the primary pulleys 20, 70, and 80 according to the first to third embodiments, a plurality of cylindrical rollers 60 are disposed in the gap between each inner shaft side plane 41 and each outer shaft side plane 56. FIG. As shown in FIG. 4, a plurality of steel balls 101 may be provided in place of the plurality of cylindrical rollers 60. At this time, the plurality of steel balls 101 are divided into three steel ball groups 102 according to the three inner shaft side planes 41 and the three outer shaft side planes 56, and each steel ball group 102 is divided into each inner ball side group 102. They are arranged in the gaps between the shaft side plane 41 and each outer shaft side plane 56. Each steel ball group 102 includes at least two steel balls 101 and is arranged in parallel in the tangential direction.

  Accordingly, when the primary movable sheave 27 is about to rotate relative to the primary shaft 25, two steel balls arranged in parallel in the tangential direction between each inner shaft side plane 41 and each outer shaft side plane 56. 101 tries to maintain the parallel state of each inner shaft side plane 41 and each outer shaft side plane 56. For this reason, the rotation of the primary movable sheave 27 relative to the primary shaft 25 is locked by a total of six steel balls 101 between the three inner shaft side planes 41 and the three outer shaft side planes 56. Accordingly, the primary movable sheave 27 is configured so as not to be displaced in the circumferential direction.

  On the other hand, when the primary movable sheave 27 is displaced relative to the primary shaft 25 in the axial direction, the primary movable sheave 27 has a movable side sliding main surface 55 that is an inner peripheral surface of the small diameter side through hole 53b. The steel balls 101 roll in the axial direction while sliding on the fixed sliding main surface 42 which is the outer peripheral surface of the primary shaft 25. Accordingly, the primary movable sheave 27 is configured to be axially displaceable by each steel ball 101 with the fixed-side sliding main surface 42 as a guide.

  Also in the above configuration, the shaft joint 35 can be configured such that the primary movable sheave 27 can be displaced in the axial direction but not in the circumferential direction with respect to the primary shaft 25 by simple processing. Each cylindrical roller 60 is in line contact with each inner shaft side plane 41 and each outer shaft side plane 56, but each steel ball 101 is pointed with respect to each inner shaft side plane 41 and each outer shaft side plane 56. Because of the contact, the load applied to each steel ball 101 is larger than the load applied to each cylindrical roller 60. For this reason, it is preferable to arrange the cylindrical roller 60 in consideration of the applied load.

  Moreover, although the shaft joint 35 of the present invention has been described as applied to the primary pulley 20, the present invention is not limited thereto, and may be applied to the secondary pulley 21.

  As described above, the present invention is useful for a shaft joint that restricts displacement in the circumferential direction and allows displacement in the axial direction, and is particularly suitable for application to a pulley.

1 is a schematic configuration diagram illustrating a drive system of a vehicle to which a belt type continuously variable transmission having a primary pulley according to a first embodiment is applied. 1 is an external perspective view showing a primary pulley according to Embodiment 1. FIG. 1 is an exploded perspective view of a primary pulley according to a first embodiment. FIG. 3 is a half sectional view in the radial direction of the primary pulley according to the first embodiment. FIG. 3 is a cross-sectional view in the axial direction of the primary pulley according to the first embodiment. It is the external appearance perspective view which decomposed | disassembled the primary pulley which concerns on Example 2. FIG. 7 is an external perspective view of a roller holding member according to Embodiment 2. FIG. FIG. 10 is a front view in the axial direction of a roller holding member according to a modification of Example 2. It is the external appearance perspective view which decomposed | disassembled the primary pulley which concerns on Example 3. FIG. It is the external appearance perspective view which decomposed | disassembled the primary pulley which concerns on the modification of Example 3. FIG. It is an external appearance perspective view of the flat washer with a nail | claw used for the primary pulley which concerns on the modification of Example 3. It is sectional drawing in the axial direction of the primary pulley which arrange | positioned the several steel ball.

Explanation of symbols

8 Belt type continuously variable transmission 20 Primary pulley 21 Secondary pulley 22 Belt 25 Primary shaft 26 Primary fixed sheave 27 Primary movable sheave 30 Secondary shaft 31 Secondary fixed sheave 32 Secondary movable sheave 35 Shaft joint 41 Inner shaft side plane 42 Fixed side sliding Main surface 50 Cylindrical portion 51 Annular portion 53 Through-hole 53a Large-diameter side through-hole 53b Small-diameter-side through-hole 55 Movable-side sliding main surface 56 Outer shaft-side plane 60 Cylindrical roller 61 Cylindrical roller group 63 Stopper 70 Primary pulley (implementation) Example 2)
71 Roller holding member 72 Roller accommodating portion 73 Roller accommodating portion group 75 Divided holding member 80 Primary pulley (Example 3)
81 Flat washer 90 Primary pulley (Modification)
91 Claw part 101 Steel ball 102 Steel ball group H Center line L Separation distance

Claims (9)

In a shaft joint that restricts relative displacement in the circumferential direction between the inner shaft and the outer shaft, and allows relative displacement in the axial direction between the inner shaft and the outer shaft,
A plurality of rotating bodies disposed in a circumferential direction of a gap between the inner shaft and the outer shaft, and capable of rolling in an axial direction by rolling contact with an outer peripheral surface of the inner shaft and an inner peripheral surface of the outer shaft;
A plurality of inner-axis-side planes formed on the outer peripheral surface of the inner shaft to which the rotating bodies are in rolling contact, and extending in the axial direction of the inner shaft;
A plurality of outer-axis-side planes that are formed on the inner peripheral surface of the outer shaft to which the rotating bodies are in rolling contact, face in parallel to the inner-axis-side planes, and extend in the axial direction of the outer shaft. A shaft joint characterized by that.   2. The shaft joint according to claim 1, wherein each of the rotating bodies is formed in a cylindrical shape whose axis is perpendicular to the axial direction of the inner shaft.   The plurality of rotating bodies are arranged in a plurality of rotating body groups according to the plurality of inner-axis-side planes and the plurality of outer-axis-side planes, and the plurality of rotating bodies in each of the rotating body groups. The shaft joint according to claim 2, wherein the shaft joints are arranged in parallel in the axial direction of the inner shaft.   Each of the rotating bodies is formed in a spherical shape, and the plurality of rotating bodies are divided into a plurality of rotating body groups according to the plurality of inner shaft side planes and the plurality of outer shaft side planes. The shaft joint according to claim 1, wherein the plurality of rotating bodies in each of the rotating body groups are arranged side by side in a circumferential direction of the inner shaft.   5. The rotating body holding member that is provided in the gap between the inner shaft and the outer shaft and that holds the posture of each rotating body, further comprising: Shaft coupling.   The shaft joint according to claim 5, wherein the rotating body holding member is configured to be separable.   The shaft joint according to claim 3, further comprising a washer interposed between the rotating members of the rotating member group. A shaft joint according to any one of claims 1 to 7,
The inner shaft;
A fixed sheave integrally formed at one end of the inner shaft;
A pulley comprising: a movable sheave disposed opposite to the fixed sheave and having an outer portion and an annular portion formed integrally with one end portion of the outer shaft.   The pulley according to claim 8, wherein the movable sheave further includes a stopper that is disposed at the other end portion of the outer shaft and prevents deviation of the rotating bodies.

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