JPH03199719A - Ball spline device - Google Patents

Abstract

PURPOSE:To decrease a diameter of outer side balls so as to generate uniform wearing by arranging a plurality of balls in opposed recessed grooves provided in both boss parts of the first member having the boss part and the second member having the boss part fitted to the peripheral surface of the concerned boss part of the first member. CONSTITUTION:A primary pulley 3 is provided with a fixed sheave 3a, boss part 3a1 thereof, movable sheave 3b and a boss part 3b1 thereof. Many recessed grooves 58 are formed in the peripheral surface of the boss part 3a1, and many recessed grooves 59 are formed in the internal peripheral surface of the opposed boss part 3b1. Balls 60A to 60Z are arranged between both the recessed grooves 58, 59. At least the balls 60A, 60Z in the outermost side of the balls are formed in a diameter smaller than that of the other balls. By such constitution as mentioned, stress of the balls 60A, 60Z in both the outer sides is prevented from increasing by uniformly generating stresses PA to PZ applied to each ball by moment M generated in the movable sheave 3b. Accordingly, a life is extended by making wearing of the ball uniform.

Description

DETAILED DESCRIPTION OF THE INVENTION (Field of Industrial Application) The present invention relates to a ball spline device for relatively moving a first member and a second member in the axial direction.

(Prior Art) Conventionally, automatic transmissions incorporating belt-type continuously variable transmissions have been provided as automotive transmissions in order to improve fuel consumption.

In the above-mentioned belt type continuously variable transmission, a belt is stretched between a primary pulley and a secondary pulley, each consisting of two sheaves supported by a shaft and relatively movable in the axial direction. Continuous speed change is achieved by adjusting the axial distance between the sheaves.

Of the two sheaves, a groove with a semicircular cross section extending in the axial direction is formed on the inner peripheral surface of the boss portion of the movable sheave, and a groove with a semicircular cross section extending in the axial direction is formed on the outer peripheral surface of the boss portion of the fixed sheave. Grooves are formed, and a ball is inserted into the space formed by the grooves to prevent relative rotation.

(Problem B to be Solved by the Invention) However, in the ball spline device having the above configuration, the movable sheave is fitted into the fixed sheave boss portion or the shaft by sliding friction, and a belt is stretched between the two sheaves. Since the torque is transmitted by the movable sheave in the axial direction, a large 11! Not only does frictional resistance occur, but also a moment is generated in the direction between the sheave shafts based on the tension of the belt.

The state in which this moment occurs will be explained using the primary pulley as an example.

FIG. 5 is an explanatory diagram of moments generated in the above ball spline device.

In the figure, the primary pulley 3 has a fixed sheave 3a and a movable sheave 3b that is movable in the axial direction with respect to a boss portion 3a+ of the fixed sheave.

The boss portion 3al extends toward the movable sheave 3b, and its inner peripheral surface 3at fits into the primary shaft.

Further, a large number of grooves 58 are formed on the outer peripheral surface 3as.

On the other hand, a large number of grooves 59 are similarly formed on the inner peripheral surface 3bx of the boss portion 3b of the movable sheave 3b. A ball 60 is disposed between both grooves 58 and 59.

Incidentally, a belt 9 is provided between the fixed sheave 3a and the movable sheave 3b, and is stretched between the primary pulley 3 and the secondary pulley.As torque is transmitted by the belt 9, the belt 9 is rotated as shown by arrow F in the figure. You will receive such power.

As a result, a moment as shown by arrow M is generated in the movable sheave 3b. The moment) M generates stress P in the ball 60 between the boss portion 3b+ of the movable sheave 3b and the boss portion 3a of the fixed sheave 3a. and multiple balls 6
Outermost ball 6 of 0A, 60B, ...602
The largest stress P MAX is applied to 0A and 60Z, and smaller stress is applied toward the inner side.

Therefore, while using the ball spline device, the balls 60 are worn or damaged, making it impossible to smoothly transmit rotation, and also making it impossible to increase the capacity of the sheave, resulting in an increase in the size of the device. .

Therefore, a ball spline device is provided in which the balls are preloaded and placed in the groove, but this increases the frictional resistance between the balls and the groove, increases the temperature of the ball spline device, and increases the lifespan of the ball spline device. It also becomes shorter.

In addition, while increasing the ball diameter, it is also possible to lengthen the boss section in the axial direction to reduce the stress caused by the moment load, but this increases the size of the ball spline device and increases its weight, which may adversely affect the transient characteristics of shifting. be.

The present invention solves the above-mentioned problems of the conventional ball spline device, and allows smooth transmission of rotation without the balls being worn or damaged while the ball spline device is in use. It is an object of the present invention to provide a ball spline device whose capacity can be increased and whose size can be reduced.

(Means for Solving the Problems) For this purpose, the ball spline device of the present invention includes a first member having a boss portion, a first member that is fitted onto the outer circumferential surface of the boss portion of the first member, and A second member having a boss portion at a position corresponding to the first member and receiving a moment load relative to the first member is provided, and the boss portions of the first member and the second member are opposed to each other. A plurality of grooves are formed in the axial direction on the surface.

A plurality of balls are accommodated in the groove, and means for preventing the balls from falling out are provided at both ends of the groove.

In the balls, at least the outermost ball has a smaller diameter than the other balls in the axial direction of the groove.

Further, the diameter of the ball may gradually increase from the outermost side to the innermost side in the axial direction of the groove.

In addition, a continuously variable transmission system in which a belt is stretched between a pair of pulleys consisting of a fixed sheave and a movable sheave, and the effective diameter of the belt is changed by changing the distance between the movable sheave and the fixed sheave. In the ball spline device used in the invention, the first member is a fixed sheave, and the second member is a movable sheave.

(Operations and Effects of the Invention) According to the present invention, as described above, the first member has a boss portion, and the first member is fitted to the outer circumferential surface of the boss portion of the first member, and is located at a position corresponding to the boss portion. a second member having a boss portion thereon and receiving a moment load relative to the first member;
A plurality of grooves are formed in the axial direction on opposing surfaces of the boss portions of each of the first member and the second member, and a plurality of balls are accommodated in the grooves. Means for preventing the balls from falling out is provided at both ends of the groove, and since the diameter of at least the outermost ball is smaller than the diameter of the other balls in the axial direction of the groove, the diameter of the second ball is smaller than that of the other balls. When a moment is generated in the member, the stress applied to the outermost ball becomes smaller.

Therefore, only the outermost balls are not subjected to excessive frictional resistance, are not worn out or damaged, and the durability of the ball spline device can be improved.

Moreover, since it is possible to reduce the stress on the outermost ball, the capacity of the ball spline device can be increased and the device can also be made smaller.

Further, if the diameter of the ball is gradually increased from the outermost side to the innermost side in the ring direction of the groove, the stress applied to all the balls can be made almost equal. Therefore, wear is uniform between the balls.

In addition, a continuously variable transmission system in which a belt is stretched between a pair of pulleys consisting of a fixed sheave and a movable sheave, and the effective diameter of the belt is changed by changing the distance between the movable sheave and the fixed sheave, thereby continuously changing the speed. In the ball spline device used for this purpose, the balls are not worn or damaged, and the movable sheave can be moved smoothly.

Moreover, it is possible to increase the sheave capacity,
It becomes possible to downsize the continuously variable transmission.

(Example) Hereinafter, an example of the present invention will be described in detail with reference to the drawings.

FIG. 1 is a cross-sectional view of a pulley of a ball spline device of the present invention, FIG. 2 is a cross-sectional view of a continuously variable transmission in which the ball spline device of the present invention is used, FIG. The figure is a 1-1 sectional view of FIG.

In FIG. 2, the continuously variable transmission A has a transformer coupling case 13 which is divided into three parts and consists of a torque converter case 13a, a center case 13b and a rear case 13c.
Human power shaft 3 that constitutes the output shaft of the fluid torque converter 31
2 and the primary shaft 1 of the continuously variable transmission 12 are rotatably supported on the same axis to constitute a first shaft, and the secondary shaft 2 of the continuously variable transmission 12 integrally formed with the output gear 33 rotates. It is freely supported and constitutes a second shaft.

Further, on the first shaft, a forward friction clutch C1 and its hydraulic actuator 37 for operating the dual planetary gears constituting the forward/reverse switching device 1f35, and a hydraulic pump 39 are arranged between the torque converter 31 and the primary pulley 3. ing.

The torque converter 31 has a torque converter housing 31a, and the torque converter housing 3
An engine crankshaft 40 is connected to 1a, and a pump impeller is fixed thereto.

Further, a turbine runner is disposed opposite to the pump impeller, and a stator that is prevented from rotating in one direction is disposed between the pump impeller and the turbine runner.

Further, a lock-up clutch 41 is arranged in parallel with the turbine runner in the converter housing 31a, and the lock-up clutch 41 is connected and released by switching the supply oil path by a hydraulic control device (not shown). It is connected to an input shaft 32, which serves as an output shaft of the torque converter, via two types of damper springs.

The forward/reverse switching device 35 includes a dual planetary gear 3 consisting of a carrier 36b and a ring gear 36c that support two types of binions that mesh with a sun gear 36a.
6, the sun gear 36a is connected to the input shaft 32.
spline connection.

In addition, the carrier 36b has an example plate having a forward flange C.
1 to the human power shaft 32, and the other side plate is connected to the primary pulley 3 via the pressure regulating cam mechanism 10, and the ring gear 36c is connected to the reverse friction brake B2.

Furthermore, the advancing flange C1 is interposed between a drum member 42 connected to the carrier 36b and a hub member connected to the human power shaft 32, and a hydraulic actuator 37 is disposed on the drum member 42. There is.

Therefore, the hydraulic actuator 37 is in a non-rotating state in the neutral state, and it is possible to eliminate the influence of centrifugal hydraulic pressure when hydraulic pressure is supplied to the actuator 37 during forward (D range) operation.

Further, the reverse brake B2 is disposed between the hub portion of the ring gear 36c that protrudes in the outer diameter direction and the inner wall of the case 13, and the brake hydraulic actuator 45 is attached to the support wall 13d of the case. It is arranged.

Further, a protruding part is formed to protrude from the bearing annular part of the support wall 13d, and a number of return springs are arranged in a contracted state between the protruding part and the back surface of the piston member, and these protruding parts The return spring is disposed in a space with a U-shaped cross section formed on the outer diameter of the ring gear 36c, wrapping around the planetary gear 36 in the axial direction, thereby reducing the axial dimension. There is.

On the other hand, as shown in FIG. 3, the pressure regulating cam mechanism 1O is arranged between the input end cam piece 10a and the output side cam piece 10b whose opposing end surfaces are formed in a wave shape, and the end faces of both cam pieces 10a and lob. It consists of a roller 10c, the input side cam 10a is spline connected to the other side plate of the carrier 36b, and is threadedly connected to the primary shaft 1, and the output side cam piece 10b is connected to the fixed sheave 3a of the primary boot. It is spline-connected and abuts against the fixed sheave 3a via a disc spring 45.

Therefore, the torque from the carrier 36b is transmitted to the primary pulley 3 via the pressure regulating cam mechanism 10, and the pressure regulating cam mechanism IO generates an axial force corresponding to the transmitted torque, and transfers the axial force to the fixed sheave. Acts on 3a.

Further, the fixed sheave 3a has an annular flange 3aa extending so as to cover the pressure regulating cam mechanism 10, and the flange 3a
a supports the radial load acting on the fixed sheave 3a by being supported by a roller bearing 15 mounted on the case support wall 13a. Therefore, the pressure regulating mechanism l
The axial force due to O is not affected by the radial load.

The case support wall 13d includes an annular portion 13d+ that supports the roller bearing 15 and a support portion 13d extending from approximately the center of the annular portion 13dl.
d! Since it extends from the center, it has an advantageous structure in terms of strength so that the radial load from the pulley 3 does not act as a moment, and as a result, it is constructed with a relatively thin wall.

In addition, the belt continuously variable transmission 12 is a primary boot I73.
, a secondary pulley 5 and a belt 9 wrapped around both pulleys 3.5, and both boos 173.5 are connected to fixed sheaves 3a, 5a and movable sheaves 3b, 5, respectively.
Consists of b. Note that the belt 9 has a large number of metal pieces, and when the large number of pieces contact the primary pulley 3 and the secondary boot I75 in a lubricated state and torque is transmitted, the Wl friction between the pieces and the pulley is Becomes relatively small.

Therefore, the angle of the contact surface between the bridge and the pulley is set to be larger than the static HW1 angle.

The cross section of the pulley will be explained with reference to FIGS. 1 and 4.

In the figure, the primary pulley 3 has a fixed sheave 3a and a movable sheave 3b which is movable in the axial direction with respect to a boss portion 3a+ of the fixed sheave.

The boss portion 3a extends toward the movable sheave 3b,
Its inner circumferential surface 3az fits into the primary shaft.

Further, a large number of grooves 58 are formed on the outer circumferential surface 3a3, and the grooves 58 form protrusions 58a extending in the axial direction at six locations at equal intervals in the circumferential direction.

On the other hand, the inner peripheral surface 3b of the boss portion 3b+ of the movable sheave 3b.

A large number of grooves 59 are also formed in the same manner. Further, the grooves 59 are formed at six equally spaced locations in the circumferential direction to form protrusions 59a extending in the axial direction.

A ball 60 is disposed between both grooves 58 and 59,
A retainer 81 , 82 is provided to hold each ball 60 .

In this way, the boss portion 3b of the movable sheave 3b is supported on the outer peripheral surface of the fixed sheave 3a via multiple rows of ball spline mechanisms (linear ball bearings) 48 so as to be movable only in the axial direction. The movable sheave 3b is fitted into the fixed sheave boss portion 3a+ only through the ball 60 without receiving sliding frictional resistance.

Kokote, each, JF-R60A, 60B, 60C16
0z, at least the outermost balls 60A, 602(7) in the axial direction of the grooves 58, 59, D! The diameter of the other holes 60B, 60C... is smaller than DC, and the stress Pa applied to the balls 60A, 60z due to the moment M load generated on the movable sheave 3b.
, Pg are prevented from becoming larger than the stresses Pa, Pc, . . . applied to the other balls 60B, 60C, .

Alternatively, the diameter may be gradually increased from the outermost balls 60^, 60Z to the innermost ball 6ON. In that case, each ball 60A, 60B, 60C,
...The stress applied to 60Z can be made almost uniform.

That is, when a small moment is applied, stress is first applied to the innermost balls, and as the load increases, stress is applied to the outermost balls 60A, 60Z.

The moment capacity M, which sets the ball diameters Da, Di, . . . D2 at that time, is expressed by the following equation.

Me =2K(L-PA+4.-Pa-...+f
f1s-PN) And the stress when using the same ball is PM
= (f!N/1m) ””Pa.

The ball diameters DA, D, . . . , D2 are set based on transmission torque, preload, etc., at the time of maximum moment action, or on a load condition set in consideration of life.

Note that the configuration of the pulley portion described above can be applied not only to the primary pulley but also to the secondary pulley.

Further, as shown in FIG. 2, the boss portion 3 of the fixed sheave 3a
The inner circumferential surface of a+ is fitted onto the primary shaft 1 (FIG. 2) so as to form lubricating oil films 21 and 22.

A ball screw device 6 constituting an actuator mechanism is disposed at the back of the movable sheave 3b.

The ball screw device 6 is composed of a male threaded portion 6a, a female threaded portion 6b, and a ball, and is of a circulette type in which the balls are circulated in a return passage. moreover,
The male screw portion 6a of the ball screw device 6 has its rear end fixed to an adjustment member 49 that is restrained and supported by the shoulder portion of the case 13 in the axial and radial directions.

The groove member 49 has a groove formed on its inner peripheral surface, and the roller bearing I6 is directly mounted in the groove. The roller bearing 16 has a cylindrical inner race 50 fitted to the boss portion 3a+ of the fixed sheave 3a.
The fixed sheave 3a is in contact with the roller bearing 15 and the adjustment member 49 supported by the support wall 13d.
case 1 by the roller hair ring 16 supported by
Directly supported by 3. Further, a screw a is formed at the tip of the fixed sheave boss portion 3a, and a nut member 51 is screwed onto the screw a to prevent the inner race 50 from coming off.

On the other hand, a worm wheel 49a is formed on the I-loading member 49, and a worm (not shown) is meshed with the worm wheel 49a. Based on the operation of the worm, the adjusting member 49 rotates to rotate the ball screw device 6. male threaded part 6a
By rotating the belt 9 relative to the female threaded portion 6b, the initial tension of the belt 9 and the running center of the belt can be adjusted.

Further, one end of the female threaded portion 6b of the ball threaded device 6 extends obliquely in the outer radial direction to form a gear portion 52, and the concave spherical inner peripheral surface of the gear portion 52 and the thrust ball bearing 53
A self-aligning mechanism is formed by the convex spherical outer peripheral surface of the race 53a, and the ball bearing 53 supports the thrust force between the back surface of the movable sheave 3b and the female threaded portion 6b.

Further, an elastic spring made of a predetermined number of disc springs is connected between the support plate 55, which is prevented from moving in the axial direction by the nut member 51 via the inner race 50 of the roller bearing 16, and the back surface of the movable sheave 3b. A biasing member 56 is disposed, and the elastic biasing member 56 carries a part of the belt constriction load and reduces the supporting load of the ball racing device 6 and the thrust ball bearings 53, 57.

Further, a thrust support member 56a having a convex spherical surface is fixed to a flange portion formed at the tip of the primary shaft l, and the thrust support member 56a having a convex spherical surface and the concave spherical surface of the race 57a of the thrust ball bearing 57 automatically The ball bearing 57 constitutes an alignment mechanism, and supports the thrust force between the thrust support member 56a and the adjustment member 49.

Note that the nut member 51 is arranged to wrap around the inner diameter portion of the thrust ball bearing 57 in the axial direction,
The inner race 50 is prevented from coming off by preventing the inner race 50 from becoming elongated in the axial direction, and the support plate 5 is
The supporting plate 55 is also reliably prevented from jumping out in the axial direction outward, and the support plate 55 comes into contact with the end of the boss portion 3bt of the movable sheave 3b, thereby forming a mechanical stopper for the movable sheave 3b.

Thereby, for example, there is no need to specially provide a stopper on the non-circular gear portion, etc., and excessive movement of the movable sheave 3b can be prevented, thereby preventing control failure.

On the other hand, the fixed sheave 5a of the secondary pulley 5 has an annular flange 5aa formed on its back surface, similar to the above primary side, and the flange 5aa contacts a roller bearing 17 supported by the case 13. .

Further, an output gear 33 is provided at the base end of the secondary shaft 2.
are integrally formed, and the roller bearing 2
A fixed sheave 5 is supported on the secondary shaft 2 via two needle bearings 23 and 25 arranged at a predetermined interval.
The boss portion 5a+ of a is rotatably supported.

Further, the case 13 supports an adjustment member 61 whose movement in the radial and axial directions is restricted.
A groove is formed on the inner peripheral surface of the bracket 1, and a roller bearing 19 is directly mounted in the groove.

The roller bearing 19 rotatably supports the expanded diameter portion 2a of the secondary shaft 2.

Therefore, on the secondary side, shaft 2 is connected to output gear 3.
It is supported by the case 13 by a roller bearing 1920 placed on both sides of the case 13. And fixed sheave 5a
The back side is attached to the case 13 by the roller hair ring 17.
The shaft 2 is supported by two needle bearings 23 and 25 at the boss portion 5al.

Further, a pressure regulating cam mechanism 11 similar to that on the primary side is disposed on the inner diameter portion of the back surface of the fixed sheave 5a. The cam machine 111
One cam piece 11a of the cam piece 1 is spline engaged with the shaft 2, the other cam piece 11b is spline engaged with the fixed sheave 5a, and a roller 11c is interposed between both cam pieces.

A screw 2c is formed at the tip of the shaft 2, and a nut member 62 is screwed into the screw to engage the cam mechanism 11.
A disc spring 63 and a thrust bearing 65 are interposed between the cam piece 11a and the cover 13e fixed to the case 13.

Further, the boss portion 5b of the movable sheave 5b is slidably fitted into the boss portion 5a+ of the fixed sheave 5a by a ball spline 66 via only a ball 60 (FIG. 1). A ball screw device 7 is disposed on the back side of the movable sheave 5b, and its male threaded portion 7a is fixed to the m-joint member 61, and the adjustment member 61 is adjusted to the primary side based on the rotation of the worm. Together with the adjustment member 49, the initial tension and running center line of the belt 9 can be adjusted.

Further, a gear portion 69 that serves as a self-aligning mechanism is formed in the female threaded portion 7b, similar to the above-mentioned primary side, and a race 70a and a back surface of the movable sheave 5b, which are part of the self-aligning mechanism, are formed. A thrust ball bearing 70 is interposed.

Further, a screw d is formed at the tip of the boss of the fixed sheave 5a, and a support plate 71 is fixed to the screw d by screw connection. The support plate 7I and the movable sheave 5b
An elastic biasing member 74 similar to that on the primary side is disposed between the primary side and the rear side.

Further, the support plate 71 is firmly fixed by screw connection, and when the movable sheave 5b is fully extended, the sheave boss end comes into contact with the support plate 71, thereby forming a mechanical stopper that restricts further movement.

The above-mentioned threaded coupling portion is formed on the side surface of the shaft enlarged diameter portion 2a, and is disposed substantially ramped in the axial direction on the inner diameter side of the adjustment member 61 by a groove, and the threaded coupling portion exists. will not become longer in the axial direction.

Further, a thrust support plate 72 having a convex spherical support surface is fixed to the side surface of the output gear 33, similar to the primary side, and the thrust support plate 72 is connected via a race 73a which together with the thrust support plate 72 constitutes a self-aligning mechanism. With the thrust support plate 72!
A thrust ball bearing 73 is interposed between the j1 node member 61 and the back surface thereof.

A sleeve-shaped parking gear 98 is provided between the output gear 33 and the thrust support plate 72. Fuhai parking gear 98 is a thrust pole bearing 73
The thrust force transmitted through the race 73a and the thrust support plate 72 is transmitted to the output gear 33.
I try to accept it. Since a space 99 is formed on the rotation center side of the parking gear 98, weight reduction can also be achieved.

Further, as shown in FIG. 2, an operating device 75 is disposed at a portion where the primary shaft 1 and the secondary shaft 2 form a triangle. The operating device 75 is case 1
The first countershaft 76 has a first countershaft 76 and a second countershaft (not shown) which are supported by the second countershaft 76 via a bearing.The first countershaft 76 has a large gear 79
A gear unit 79 having a small gear 79b and a small gear 79b is rotatably supported, and a large gear 80 is integrally fixed to one end thereof, and a non-circular gear 83 is fixed to the other end.

The gear unit 79 rotatably supported on the first countershaft has its large gear 79a meshing with the gear portion 52 of the primary ball screw device 6, and rotation is transmitted from the electric motor 86. The small gear 79b meshes with the large gear fixed to the second countershaft, and the noncircular gear fixed to the second countershaft meshes with the gear 87 fixed to the second countershaft. The gear 83, the large gear 80, and the speed increasing device in the transmission path from the gear unit on the second countershaft (therefore, the speed reduction device in the transmission path from the gear part 52 of the ball screw device 6) are configured. .

On the other hand, as shown in FIG. 2, an electric motor 86 for speed change operation is fixed outside the case 13, and the electric motor 86 has a brake that can hold it in a predetermined position when not energized. There is.

The output gear 89 of the motor 86 is connected to the reduction gear train 9.
0 and the above-mentioned ball screw device 6 through the gear 87.
Operation device ml that interlocks 7! Power is transmitted to 75.

Further, the output gear 33 formed on the secondary shaft 2 meshes with a large gear 93 fixed to the intermediate shaft 92. Further, a small gear 95 is formed on the intermediate shaft 92, and the gear 95 meshes with a ring gear 97 fixed to a differential gear device 96 to constitute a speed reduction device. Also, differential gearing! From F97 left and right front axle shaft 96 /! , 96r extends.

Next, the operation of this embodiment will be explained.

The rotation of the engine crankshaft 40 is transmitted to the input shaft 32 via the fluid torque converter 31 when the vehicle starts. That is, the rotation of the engine crankshaft 40 is transmitted from the pump impeller to the turbine launch via oil flow, and torque is increased by the stator.

At this time, the torque increased due to the maximum stall state while the vehicle is stopped is transmitted to the input shaft 32, and as the relative speed ratio between the pump impeller and the turbine runner decreases as the vehicle starts, Torque increase is tapered off.

The increased torque of the input shaft 32 is transferred to the forward/reverse switching device 35.
The increased torque is transmitted to the pressure regulating cam mechanism 10 of the belt type continuously variable transmission 1f12, and the pressure regulating cam mechanism 10 applies a strong axial force to the fixed sheave 3a of the primary boot U3 in response to the increased torque.

Further, the torque transmitted to the primary pulley 3 is transmitted to the secondary pulley 5 via the belt 9, and is transmitted to the secondary shaft 2 via the pressure regulating cam structure 11, and the secondary pulley 5 also has a strong torque corresponding to the increased torque. Apply axial force.

Furthermore, when the vehicle speed increases and the fluid torque converter 31 reaches the cambling range, almost the same torque as the engine crankshaft 40 is output to the input shaft 32, and the torque of the input shaft 32 is similarly applied to the pressure regulating cam mechanism 10. .11, and these pressure regulating cam devices 1110.11 generate a relatively small axial force in response to the torque.

Then, when the input shaft 32 reaches a predetermined speed, the lock-up clutch 41 is engaged, and thereafter torque is transmitted by mechanical engagement of the lock-amp clutch 41.

When the vehicle is stopped, the input shaft 32 is rotating at a predetermined speed, but the cylinder member 42, which is interlocked with the vehicle via the belt-type continuously variable transmission 12, the dual planetary gear 36, etc., is in a stopped state. It is in. In this state, when the operator operates the shift lever from the neutral position to the forward position, the hydraulic pressure from the hydraulic pump 39 is appropriately regulated by a hydraulic control device (not shown), and then supplied to the hydraulic actuator 37 via an oil path. and moves the piston member toward the friction clutch CI.

As a result, the forward friction clutch C1 is engaged rapidly and without causing a large shift shock, and the rotation of the input shaft 32 is transmitted to the carrier 36b of the dual planetary gear 36 via the clutch C1.

The rotation of the carrier 36b, together with the rotation of the sun gear 36a connected to the input shaft 32, is transmitted to the input shaft cam piece 10a of the pressure regulating cam mechanism 10 by integrating the planetary gear 36.

Further, when the operator operates the shift lever from the neutral position to the reverse position, hydraulic pressure from the hydraulic control device is supplied to the brake hydraulic actuator 45. As a result, the piston member moves and the reverse friction brake B2
Similar to the forward friction clutch CI, the clutch engages with a quick response and without causing a large shift shift.

In this state, the rotation of the input shaft 32 is transmitted to the sun gear 36a of the dual planetary gear 36, and the ring gear 36c is fixed by the brake B2.
The rotation of the pinion is transmitted to the carrier 36b as reverse rotation, and the input end cam piece 10 of the pressure regulating cam mechanism 10
transmitted to a.

The torque transmitted to the input side cam piece 10a is transmitted to the fixed side sheave 3a of the primary pulley 3 via the roller 10c and the output side cam piece 10b, and is also transmitted to the axial force generation function of the pressure regulating cam mechanism 10. Based on this, an axial force corresponding to the transmitted torque is applied to the stationary sheave 3a.

At this time, the fixed sheave 3a has a flange 3an on the back side directly supported by the case support wall 13a via the roller hair ring 15, and a boss 3at of the fixed sheave 3a supported by the roller bearing 16.
It is supported by the case 13 via the adjusting member 49, and the large radial load caused by the belt tension is directly borne by the case 13, and no frictional force is exerted between it and the pressure regulating cam mechanism 10.

Further, the torque of the fixed sheave 3a is transmitted to the movable sheave 3b via the ball spline mechanism 48, and the belt 9 is clamped by the axial force based on the pressure regulating cam mechanism 10, and the secondary boot is transferred via the belt. +J 5 is transmitted. At this time, the axial reaction force from the belt 9 is applied to the fixed sheave 3.
a and the movable sheave 3b, the axial force from the fixed sheave 3a is carried by the primary shaft l via the pressure regulating cam mechanism 10, and the axial force from the movable sheave 3b is
Thrust ball bearing 53, race 53a of self-aligning mechanism, gear part 52, ball screw device 6 in a predetermined state
,! [! F1 member 49, thrust ball bearing 57
and the race 57a of the self-aligning mechanism, the thrust support member 5
Flange portion 1 formed on shaft 1 via 6a
d, which causes the axial force to be applied to the primary shaft 1
is received in a closed loop that acts as a tensile stress.

A part of the axial force acting on the movable sheave 3b is directly received from the rear surface of the sheave by the boss portion 3a+ of the fixed sheave 3a via the elastic biasing member 56 and the support plate 55, and is also received by the thrust bearing 53, 57 and the ball. The axial force acting on the screw device 6 is reduced.

Then, the torque from the belt 9 is transmitted to the secondary pulley 5 and further transmitted to the secondary shaft 2 via the pressure regulating cam mechanism 11. At this time, similarly to the primary side, the pressure regulating cam mechanism 11 generates an axial force corresponding to the transmitted torque, and applies this axial force to the fixed sheave 5a to clamp the belt 9, and also acts on the fixed sheave 5a. The axial reaction force is carried by the nut 62 directly on the shaft 2, and the axial reaction force acting on the movable sheave 5b is generated by the thrust ball bearing 70, the race 70a of the self-aligning mechanism, the gear part 69,
The rotation is performed by the gear 33 formed on the shaft 2 via the ball screw device 7, the adjustment member 61, the thrust ball bearing 73, the race 73a of the self-aligning mechanism, and the thrust support member 72.

Similarly, part of the axial force acting on the movable sheave 5b is directly transmitted to the boss portion 5 of the fixed sheave 5a via the elastic biasing member 74.
a. can be received directly.

At this time, as with the primary side, the secondary boot IJ 5
However, on the back side of the fixed sheave 5a where the pressure regulating cam mechanism 11 is located, the flange 5an is supported by the case 13 via a roller bearing 17, and the above-mentioned radial load is applied. The load does not affect the pressure regulating cam mechanism 1, and the tip of the secondary shaft 2 is directly supported by the case 13 via the roller bearing 20, and the expanded diameter portion 2
a is supported by the case 13 via the roller bearing 19 and the 1mllfj member 61, and the shaft 2 and the boss portion 5a of the fixed sheave.

Two needle bearings 2 with a predetermined interval between
3.25, and even if a radial load due to the output gear 33 acts on the shaft 2, the radial load does not act as a frictional force between the shaft 2 and the fixed sheave 5a.

Therefore, the entire torque transmitted to the secondary pulley 5 is transmitted to the secondary shaft 2 via the pressure regulating cam mechanism 11, and an axial force that accurately corresponds to the transmitted torque is applied to the fixed sheave 5a, thereby ensuring proper belt narrowing. Pressure is maintained.

Note that the roller bearing 16.19 directly held in the groove formed in the adjustment member 49.61 is connected to the shaft 1.2.
The lubricating oil scattered from all directions is collected in the groove, and a good lubrication state is maintained, allowing smooth rotation of the boot and shaft to be maintained for a long period of time.

Also, based on the speed change command from the control section, the electric motor 86
When the large gear 79a rotates, the large gear 79a loosely engaged with the first countershaft 76 via the deceleration bag W90 rotates, and the gear portion 52 that meshes with the gear 79a rotates the female screw portion 6b integral therewith. Then, in the adjusting member 49, the female threaded portion 6 is rotated relative to the male threaded portion 6a, which is prevented from rotating.
b moves in the axial direction and moves the movable sheave 3b via the self-aligning thrust ball bearing 53 to change the belt effective diameter of the primary boo IJ 3.

On the other hand, the rotation of the large gear 79a is significantly decelerated by the meshing of the small gear 79b of the gear unit 79 and the large gear of the second countershaft, and is transmitted to the second countershaft. The signal is transmitted to the first countershaft 76 .

Then, the decelerated rotation is transferred to the first countershaft 76.
and is transmitted to the secondary side gear part 69 via the gear unit of the second countershaft, and due to the rotation of the gear part 69, the female threaded part 7b integrated therewith is rotated relative to the fixed male threaded part 7a. It rotates and moves in the axial direction, moves the movable sheave 5b via the self-aligning thrust ball bearing 70, and changes the belt effective diameter of the secondary pulley 5. At this time, the amount of movement of the primary and secondary pulleys 3.5 and the amount of movement of the belt 9 do not correspond linearly, but the difference in the amount of re-movement is properly absorbed by transmission via the circular gear. Ru.

The rotation of the secondary shaft 2 is controlled by the output gear 33.
from the differential gear device 9 via the large gear 93 and small gear 95.
6, and is then transmitted to the left and right front axle shafts 96f96r by the differential gear device 96.

Note that the present invention is not limited to the above embodiments,
Various modifications are possible based on the spirit of the present invention, and these are not excluded from the scope of the present invention.

[Brief explanation of drawings]

FIG. 1 is a cross-sectional view of a pulley of a ball spline device of the present invention, FIG. 2 is a cross-sectional view of a continuously variable transmission in which the ball spline device of the present invention is used, FIG. The figure is a 1-1 sectional view of FIG. 1, and FIG. 5 is an explanatory diagram of the moment generated in the above ball spline device. 3a...Fixed sheave, 3a+...Boss part, 3b・
・・Movable sheave, 3b+ ・・Boss part, 58.59・
・・Concave groove, 60.60A~602・・Ball, 9・・
·belt. Engraving of the drawing, Figure 1?

Claims (4)

[Claims] (1) A first member having a boss portion, which is fitted to the outer peripheral surface of the boss portion of the first member, has a boss portion at a position corresponding to the boss portion, and has a boss portion at a position corresponding to the boss portion; a second member that receives a moment load relative to the second member; a plurality of balls accommodated in a plurality of grooves formed in the axial direction on opposing surfaces of the boss portions of the two members; What is claimed is: 1. A ball spline device, comprising means for preventing balls from falling off, and wherein the diameter of at least the outermost ball in the axial direction of the groove is smaller than the diameter of the other balls. (2) a first member having a boss portion; the first member having a boss portion that is fitted onto the outer peripheral surface of the boss portion of the first member; and having a boss portion at a position corresponding to the boss portion; a second member that receives a moment load relative to the second member; a plurality of balls accommodated in a plurality of grooves formed in the axial direction on opposing surfaces of the boss portions of the two members; What is claimed is: 1. A ball spline device comprising means for preventing the ball from falling off, and wherein the diameter of the ball is gradually increased from the outermost side to the innermost side in the axial direction of the groove. (3) Continuously variable transmission in which a belt is stretched between a pair of pulleys consisting of a fixed sheave and a movable sheave, and the effective diameter of the belt is changed by changing the distance between the movable and fixed sheaves. In the ball spline device of the device,
The fixed sheave has a boss portion, the movable sheave is fitted on the outer peripheral surface of the boss portion of the fixed sheave, and has a boss portion at a position corresponding to the boss portion, and the movable sheave has a boss portion at a position corresponding to the boss portion of the fixed sheave. A plurality of grooves are formed in the axial direction on the opposing surface of the groove, and a plurality of balls are accommodated in the groove, and means for preventing the balls from falling out is provided at both ends of the groove, and
A ball spline device for a continuously variable transmission, characterized in that the diameter of at least the outermost ball in the axial direction of the groove is smaller than the diameter of the other balls. (4) Continuously variable transmission in which a belt is stretched between a pair of pulleys consisting of a fixed sheave and a movable sheave, and the effective diameter of the belt is changed by changing the distance between the movable sheave and the fixed sheave. In the ball spline device of the device,
The fixed sheave has a boss portion, the movable sheave is fitted on the outer peripheral surface of the boss portion of the fixed sheave, and has a boss portion at a position corresponding to the boss portion, and the movable sheave has a boss portion at a position corresponding to the boss portion of the fixed sheave. A plurality of grooves are formed in the axial direction on the opposing surface of the groove, and a plurality of balls are accommodated in the groove, and means for preventing the balls from falling out is provided at both ends of the groove, and
A ball spline device for a continuously variable transmission, characterized in that the diameter of the ball gradually increases from the outermost side to the innermost side in the axial direction of the groove.