JPS622062A - Friction type continuously variable transmission - Google Patents

Abstract

PURPOSE:To control a contact arm to surely perform the follow-up action even for any moving direction of a retainer, by engaging the contact arm with V-shaped guide grooves formed in the retainer. CONSTITUTION:An inner valve 53 constituting a spool is slidably inserted penetrating through in an outer valve 52. While a contact arm 67 is integrally mounted to the inner valve 53. And the contact arm 67 slidably engages with V-shaped guide grooves 65, 66 formed on the peripheral surface of a retainer 37. By this constitution, the contact arm 67 is enabled to surely perform the follow-up action even for a movement in any direction of the retainer 37.

Description

DETAILED DESCRIPTION OF THE INVENTION "Field of Industrial Application" The present invention relates to a friction type continuously variable transmission, and particularly to a toric drive friction type continuously variable transmission.

"Prior Art" Conventionally, as a friction type continuously variable transmission, a toric drive friction type continuously variable transmission as shown in FIGS. 1 and 2 is known.

The friction type continuously variable transmission 1 includes an output shaft 2, and a concave curved surface 3a, which is attached to the output shaft 2 so as to be slidable and rotatable in its length direction, and which is similar to that seen in a rotating body having an arc as a generatrix. a rotary disk 3 for input, which is integrally attached to the output shaft 2, has a concave curved surface 4a similar to the rotary disk 3 for input, and faces the rotary disk 3 for input; a loading cam plate 6 rotatably provided on the output shaft 2 and connected via a loading cam 5 to the input rotating disk 3; On both sides of the input shaft 8 connected to the cam plate 6 via the reduction mechanism 7 and the output shaft 2,
two rollers 9 disposed in contact with the concave curved surfaces 3a, 4a of both rotating disks 3.4; and a pair of parallel retainers that rotatably support each roller 9 via an eccentric shaft 10. 11, a tie rod 12 that connects the ends of each retainer 11 and rotatably supports each retainer 11 around its length direction, and a tie rod 12 that rotatably supports the center portion of the tie rod 12 and a pivot shaft 13 disposed along the length direction of the retainer 11;
Pistons 14 provided at both ends of each retainer 11 and operated by hydraulic pressure, and a 4-way valve 15 for supplying working fluid to avoid operating these pistons 14;
A cam 17 is provided between the bushing rod 16 of the 4-way valve 15 and the retainer 11, and controls the operation of the piston 14 by feeding back the amount of rotation of the retainer 11 to the 4-way valve 15 via the bushing rod 16. It consists of

In such a friction type continuously variable transmission l, when the input shaft 8 is rotated by a prime mover or the like, the loading cam plate 6 is rotated by this rotation via the deceleration mechanism 7, and the loading cam Due to the action of the loading cam 5 as the plate 6 rotates, the input rotary disk 3 is rotated integrally, and the output rotary disk 4 is also rotated.
This causes the roller 9 to come into pressure contact with the rotary disk 4 for output, and the rotary disk 3 for input.
The rotation is transmitted to the output rotating disk 4 and the output shaft 2 via the roller 9.

Also, by operating the 4WAY valve 15, each piston 1
4 and move the respective retainers 11 in mutually opposite directions along their lengths, thereby tilting the axis of rotation of the rollers 9 and changing speed.

That is, when each retainer 11 is moved as described above, when viewed from the roller 9, as shown in FIG. The contact position A-A' with 3.4 moves to a position B-B' which is shifted from the center of rotation of the roller 9. On the other hand, during the zero period when this contact position shift occurs, the action of the loading cam 5 and the loading cam plate 6 maintains the contact between the roller 9 and both rotating discs 3.4, and the transmission of rotational force continues. Because it is being done
At the contact position BB', a frictional force as shown by arrow F in FIG. 3 acts on the roller 9.

A component force F1 of this frictional force F in the direction of the rotational axes of both rotary disks 3.4 acts on the roller 9 in the same direction at each contact position, and as a result, the roller 9 is rotated around the axis of the retainer 11. Then, it is tilted together with the retainer 11, as shown in FIG. 2, and comes into contact with both rotary disks 3.4 at portions having different diameters.

Further, along with the tilting operation, the roller 9 moves toward the contact position before movement, and as a result, the component force F1 is increased.
decreases, and at the point when the component force F1 becomes 0, the desired amount of tilting, that is, the amount of shift can be obtained. Further, the amount of tilting of the roller 9 is fed back to the 4-way valve 15 by the cam 17 as the amount of rotation of the retainer 11, and as described above, when the desired amount of tilting is obtained, the operation of each piston 14 is stopped. Thus, the above-mentioned shift amount is maintained.

"Problems to be Solved by the Invention" The present invention aims to solve the following problems in the conventional technology described above.

That is, in the conventional friction type continuously variable transmission l described above, in order to feed back the operating amount of the retainer 11 to 4WAY/< shift 15, a 4WAY valve 15 is installed on the cam surface of the cam 17 that is rotated integrally with the retainer 11. The bushing rod 16 of the push rod F'
Since the direction of movement of the bushing rod 16 and the direction of displacement of the cam surface are the same, the restraining force against movement of the bushing rod 16 in one direction, that is, movement away from the cam 17, is weak, and there is a risk of hunting, etc. This is a problem. Further, due to its structure, the 4-way valve 15 must be installed coaxially with the retainer 11, and the operating amount of the bushing rod 16 must also be secured, which restricts the layout and also It also has the problem that it tends to increase in size.

Means for Solving a Problem The present invention aims to provide a friction type continuously variable transmission that can effectively solve the problems in the conventional technology described above.
The friction-type continuously variable transmission includes, in particular, an input rotating disk that is rotatably driven by an input shaft rotatably supported by a casing, and an input rotating disk that is coaxially opposed to the input rotating disk. contact with the output rotating disk and the opposing surfaces of both rotating disks to transmit the rotation of the input rotating disk to the output rotating disk and contacting each rotating disk. A roller that changes the number of rotations transmitted to the output rotating disk by changing its position; a retainer that rotatably supports the roller; A fluid pressure actuator that moves along the tangential direction of the plate, and a valve unit that controls the operation of the fluid pressure actuator, the valve unit comprising:
an outer valve that is slidably inserted into a housing formed in the casing to form an oil passage between it and an inner wall surface of the casing; and an outer valve that is slidably inserted into the outer valve to form a spool. an inner valve that is integrally attached to the inner valve, and that is slidably engaged with a V-shaped guide groove formed on the outer circumferential surface of the retainer so as to be inclined with respect to the longitudinal direction of the retainer; and a contact arm that feeds back the amount of movement of the valve unit to the valve unit.

1. Effects The present invention, by having the above-described configuration, allows the valve unit to be integrated into the caning and to be installed close to the retainer, thereby minimizing the size of the transmission. The arm and the retainer can make contact on both sides of the retainer's operating direction, thereby eliminating play between the two as much as possible, thereby accurately feeding back the retainer's operating amount to the valve unit. .

"Embodiment" The present invention will be described in detail below based on a preferred embodiment shown in FIGS. 4 to 6.

Reference numeral 18 in FIGS. 4 and 5 indicates a friction type continuously variable transmission (hereinafter abbreviated as transmission) according to this embodiment.

The transmission 18 includes an input shaft 19 that is directly connected to a prime mover (not shown), an input rotating disk 20 that is integrally rotatably attached to the input shaft 19, and an output rotary disk 21 which is arranged opposite to the input shaft 19 and rotatably supported by the input shaft 19; and both rotary disks 20.2.
The rotation of the rotating disk 20 for input is transferred to the rotating circle Fi for output by contacting the opposing surfaces 20a, 21a of 1, respectively.
1 and a roller 22 that changes the number of rotations transmitted to the rotary disk 21 for output by changing the contact position with each rotary disk 20. Output shaft 24 connected via mechanism 23
It is equipped with.

The input horn shaft 19 has one end thereof penetrating a part of the casing C forming the outer shell of the transmission l and protruding to the outside of the casing C, and the penetrating part and the other end thereof is rotatably supported by the casing C by bearings 25 and 26 attached to the casing C.

Respective opposing surfaces 2 of rotating disks 20 and 21 for inputting ribs
0a and 21a are formed into concave curved surfaces similar to the surface shape of a rotating body with a circular arc as a generating line. Further, the input rotary disk 20 is attached to the input shaft 19 via a bearing 27 so as to be slidable in the length direction of the input shaft 19 and rotatable around a shaft. A loading cam plate 29 is connected to the side opposite to the side on which the surface 20a is formed via a loading cam 28, and the loading cam plate 29 is integrally connected to the input shaft I9. When the loading cam 28 and the loading cam plate 29 are rotated together with the human power shaft 19, a wedge action is generated between the loading cam 28 and the loading cam plate 29 with the input rotary disk 20. The rotary disc 20 for input is connected to the rotary disc 20 for input, and the rotary disc 20 for input is pressed toward the rotary disc 21 for output. On the other hand, the output rotary disk 21 has an inner circumference supported by the input shaft 19 via a bearing 30, and an outer circumference supported by the casing C via a bearing 31.
is supported by Further, a drive gear 32 is integrally provided on the side opposite to the side on which the opposing surface 21a of the output rotary disk 21 is formed.
and the driven gear 33 that meshes with the side mechanism 2.
The driven gear 33 is integrally attached to the output shaft 24 supported by the casing C via bearings 34 and 35.

The rollers 22 are arranged in two pieces, one on each side of the output shaft 24, and as shown in FIG. The eccentric shaft 3 is rotatably attached to the eccentric shaft 36.
The other end of the shaft 6 is rotatably attached to a retainer 37 provided perpendicular to the eccentric shaft 36, thereby being rotatably attached to the retainer 37.

A rotary retainer 37 is provided for each of the rollers 22, and is provided on both sides of the input shaft 19 between the two rotary disks 20.2.
They are arranged in parallel along the tangential direction of 1. and,
A thrust bearing 38 is interposed between the retainer 37 and the roller 22 to allow the roller 22 to rotate smoothly. Further, both ends of each of these retainers 37 are connected to a pair of tie rods 3 that are swingably fitted to both ends.
9, and a parallel link mechanism is formed by both retainers 37 and both tie rods 39, and a longitudinally intermediate portion of the tie rods 39 is pivoted to the casing C via a support pin 40. Connected for free movement.

Therefore, as the tie rods 39 swing, each of the retainers 37 can move in opposite directions while maintaining a mutually parallel state.

On the other hand, at each end of the retainer 37, each retainer 37
Pistons 41 to 41 for pressing and moving the
44 are arranged in series, and each of these pistons 41 to 44
The piston 41 (42-44) and the hydraulic chamber 45 (46-48) generate fluid pressure using oil as a working fluid. An actuator is configured.

As shown in FIG.
It is connected to a 4-way valve 51 that is integrally provided in the casing C as a valve unit.

As shown in FIG. 4, the 4WAY valve 51 has a housing made up of a part of the casing C, is slidably mounted on the casing C, and has the respective hydraulic chambers 45 to 48 between the casing C and the casing C. -1, 4, and an outer valve 52 forming oil passages L5, L8 communicating with an oil filter 58, which will be described later, and an outer valve 52 that is concentrically and slidably fitted inside the outer valve 52. It is equipped with an inner valve 537. The outer valve 52 has an oil supply port 60 that is connected to each of the hydraulic chambers 45 to 48 and connected to an oil pump 59 via two boats 54 and 55 and an oil filter 58 shown in FIG. Further, the inner valve 53 operates as a spool that alternately connects the ports 54 and 55 to the oil supply boat 60,
In this embodiment, the hydraulic chambers 45 and 47 and the hydraulic chambers 46 and 48, which are diagonally located, are set as a set and pressure oil is alternately supplied thereto.

Furthermore, the outer valve 52 includes a
An operating bar 61 is attached for sliding the 2 in its length direction. The operating lever 61 is made of an elastic material and is curved into a U-shape, and has protrusions 62 protruding inwardly at both ends of the operating lever 61, which are pressed into engagement grooves 63 in the circumferential direction of the outer valve 52. By matching, connection with the outer valve 52 is established. Also,
As shown in FIG. 5, the operating lever 61 is integrally attached along the radial direction to a control rod 64 provided through the casing C, and as the control rod 64 rotates, the outer valve 52 The movement is now possible.

The inner valve 53 is made to protrude to the outside from one end of the outer valve 52, and the protruding end has a guide groove 65 formed on the outer periphery of one of the retainers 37 so as to be inclined with respect to its length direction. .66 slidably engaged;
A contact arm 67 is integrally provided that slides the inner valve 53 as the retainer 37 rotates.

As shown in FIG. 4, the guide grooves 65 and 66 are formed on both sides of the retainer 37 so as to intersect at the middle when viewed from one side, and have a cross-sectional shape as shown in FIG. As shown, it is approximately V-shaped, and a flat portion 65a along the rotation direction of the retainer 37 is provided at the end thereof.
, 66a are provided.

Further, the contact arm 67 is formed of an elastic material into a U-shape (see FIG. 5), and is provided with contacts 68 at both ends thereof to be engaged in pressure contact with the guide grooves 65 and 66. As shown in FIG. 6, the contacts 68 are brought into contact with the retainer 37 at 21 locations along the length thereof when they are pressed into the guide grooves 65 and 66.

The contact arm 67 is attached to the inner valve 53 via a support rod 69 provided through the inner valve 53 in the radial direction, and is interposed between the support rod 69 and the inner valve 53. The installed spring 70 constantly urges the inner valve 53 in a direction away from the inner valve 53.

Therefore, when the retainer 37 is rotated due to the cooperation between the guide grooves 65 and 66 and the contact arm 67, the inner valve 53 is moved via the contact arm 67 along with the rotation, and the inner valve 53 is moved through the contact arm 67. The amount of rotation of the retainer 37 is 4, W
It is designed to be fed back to the AY valve 51.

On the other hand, the reference numeral 71 in FIG. 5 indicates an oil pan, and
Reference numeral 72 indicates an oil strainer.

Therefore, the transmission 18 of this embodiment configured in this manner
transmits the rotation of the human horn shaft 19 rotationally driven by the prime mover to the output shaft 24 while decelerating or increasing the speed.

That is, as the input shaft 19 rotates, the loading cam plate 29 is rotated integrally. Then, due to the rotation of the loading cam plate 29, the loading cam 1
228, the input rotary disk 20 is rotated, and the roller 22 is pressed toward the output rotary disk 21, and is positioned between the two rotary disks 20 and 21.
to hold. Therefore, the roller 22 is connected to both rotating disks 2.
0.21, the rotation of the input rotary disk 20 is transmitted to the output rotary disk 21, and the rotation of the rotary disk 21 is further transmitted to the output shaft 24 via the deceleration mechanism 23. be done.

During such a transmission operation, the input rotary disk 20
Since the input shaft 19 and the loading cam plate 29 are rotated together, the input shaft 19 rotates in substantially the same manner as the motor that rotationally drives the input shaft 19.

Therefore, since the rotational speed and torque of the prime mover are transmitted to the input rotary disk 20 almost unchanged, the performance of the toric drive continuously variable transmission is characterized by a constant maximum torque that can be transmitted. The output of the prime mover is transmitted to the subsequent equipment by making effective use of the power.

Next, the shift action will be explained as follows.

First, by rotating the control rod 64 in a desired direction and at a desired angle, 4. W A Y The outer valve 52 of the valve 51 is connected to the casing C and the inner valve 53
Move relative to. Such an outer valve 52
As a result of the movement of
8), and pressurized oil is supplied to these hydraulic chambers 45.47, and accordingly, the pistons 41.43 fitted in the hydraulic chambers 45.47 and the pistons 41.
Each retainer 37 to which 43 is connected is moved as shown by the arrow in FIG.
is rotated around its axis. As the retainer 37 moves and rotates, the rollers 22 are tilted in the same way as in the past, and the contact position with each rotary disk 20, 21 is changed, thereby performing a speed change operation. However, as the retainer 37 rotates, the guide grooves 65 and 66 formed in the retainer 37 and the guide groove 6
By the action of the contact arm 67 that engages with 5.66, 4W
The inner valve 53 of the AY valve 51 is moved in the direction of movement of the outer valve 52 to close the oil supply boat 60 and stop the supply of pressure oil to the hydraulic chambers 45 and 47. The movement and rotation of the retainer 37 is stopped, and the amount of tilting of the roller 22, that is, the amount of speed change is determined.

During such a speed change operation, the control rod 64
and the outer valve 52, the inner valve 53 and the contact arm 67, and the inner valve 53 and the retainer 37 are all engaged by elastic contact, and the contact 68 is formed on the retainer 37. Since the retainer 37 is brought into contact with the V-shaped guide grooves 65 and 66 on both sides of the retainer 37 in the direction of movement, no play or the like occurs between them, and therefore the control rod 64 can be operated manually. The amount of feedback from the retainer 37 is accurately transmitted, and the amount of shift is reliably controlled.

Furthermore, since a part of the 4-way valve 51 is formed by the casing C and is integrated into the casing C, the 4-way valve 51 can be installed in parallel near the retainer 37, resulting in a compact overall shape. Along with this, the layout of the transmission becomes easier and
The positional accuracy of the WAY valve 51 with respect to the retainer 37 and the control rod 64 is improved, and from this point of view as well, the aforementioned speed change amount can be controlled reliably. Also, 4WA
By integrating the Y valve 51 with the casing C,
The penetration portion of the casing C is reduced, thereby improving the liquid tightness inside the transmission 1.

In particular, in a toric drive transmission l as in the present application, for the purpose of increasing the frictional force between both rotating disks 20, 21 and roller 22, a friction increasing agent is added to the contact area between the two. However, if the traction oil mixes with, for example, lubricating oil outside the transmission, there is a risk that the traction oil will not be sufficiently effective.
The above-mentioned improvement in liquid tightness is extremely effective in maintaining the function of the transmission 1.

It should be noted that the various shapes and dimensions of each component shown in the above embodiments are merely examples, and it goes without saying that various changes can be made based on design requirements or the type of prime mover to be applied.

"Effects of the Invention" As explained above, the friction type continuously variable transmission according to the present invention includes a rotary disk for input rotatably driven by an input shaft rotatably supported by a casing, and a rotary disk for input. A rotary disk for output is arranged coaxially in one direction with respect to the rotary disk, and the rotation of the rotary disk for input is changed to the rotation for output by contacting the opposing surfaces of both rotary disks. A roller that changes the number of rotations transmitted to the output rotating disk by changing the contact position with each rotating disk while transmitting the rotation to the disk, a retainer that rotatably supports the roller, and a retainer that rotatably supports the roller. The valve unit Oq includes a fluid pressure actuator that is disposed at both ends and moves the retainer along the tangential direction of both rotating disks, and a valve unit that controls the operation of the fluid pressure actuator. an outer valve that is slidably inserted into a housing formed in the casing to form an oil passage between the inner wall surface of the casing; and an inner valve that is slidably inserted into the outer valve and forms a spool. When the retainer is integrally attached to the inner valve, the retainer is slidably engaged with a V-shaped guide groove formed on the outer circumferential surface of the retainer so as to be inclined with respect to the longitudinal direction of the retainer. and a contact arm that feeds the amount of movement to the valve unit, and has the following excellent effects.

■By engaging the contact arms with V-shaped guide grooves formed in the retainer, the contact arms are brought into contact with the retainer on both sides of the retainer in its movement direction, and in any direction of movement of the retainer. It is also possible to reliably follow the contact arm, accurately transmit the feedback amount from the retainer to the valve unit, and reliably control the shift amount.

■ By forming a part of the valve unit with the casing and integrating the valve unit into the case song C, the valve unit can be installed as close as possible to the retainer, and the overall transmission The shape can be made compact and the degree of freedom in the layout of the transmission can be increased.

■By integrating the valve unit and casing, the positioning accuracy of the valve unit with respect to the retainer is improved.
From this point of view as well, it is possible to ensure the control of the shift amount as described above, and to reduce the number of direct passages in the casing, thereby improving the liquid tightness inside the transmission.

[Brief explanation of the drawing]

Figures 1 and 2 show an example of the structure of a conventional toric drive friction type continuously variable transmission. Figure 1 is a longitudinal sectional view;
Fig. 2 is a sectional view taken along the line ■-■ in Fig. 1, Fig. 3 is a schematic diagram for explaining the operation of a toric drive friction type continuously variable transmission, and Figs. 4 to 6 are 4 is a longitudinal sectional view, FIG. 5 is a sectional view taken along the line ■-■ in FIG. 4, and FIG. 6 is a state of connection between the retainer and the contact arm. It is an enlarged view of the main part showing. 18...Transmission, 19...Input shaft, 20...
- Rotating disk for input, 21...Rotating disk for output, 22...Roller, 23...Deceleration mechanism,
24...Output shaft, 28...Loading cam, 29...Loading cam brake 1-13
2... Drive gear, 33... Driven gear, 36... Eccentric shaft, 3
7... Retainer, 39... Tie rod, 40...
...Support pin, 41-44...Piston,
45-48...Hydraulic chamber, 51...4WAY valve, 52...Outer valve, 53...Inner valve, 54, 55...Boat, 60...Oil supply boat , 61...operation lever, 62...
...Protrusion, 63...Engagement groove, 64・Control rond, 65/66...Guide groove, 65
a ・66a ・・Flat part, 67...Contact arm, 68...Contactor, 69...Support rod, 70...Spring, C...Casing , L, ~1,6...Oil passage.

Claims (1)

[Claims] an input rotary disk rotatably driven by an input shaft rotatably supported by a casing; an output rotary disk disposed coaxially and opposite to the input rotary disk; The rotation of the input rotating disk is transmitted to the output rotating disk by contacting the opposing surfaces of both rotating disks, and the rotation for output is transmitted by changing the contact position with each rotating disk. A roller that changes the number of rotations transmitted to the disc, a retainer that rotatably supports the roller, and a fluid that is disposed at both ends of the retainer and moves the retainer along the tangential direction of both rotating discs. comprising a pressure actuator and a valve unit that controls operation of the fluid pressure actuator,
The valve unit includes an outer valve that is slidably inserted into a housing formed in the casing to form an oil passage between the housing and an inner wall surface of the casing, and an outer valve that is slidably inserted into the outer valve. The retainer is integrally attached to an inner valve constituting the spool and is slidably engaged with a V-shaped guide groove formed on the outer circumferential surface of the retainer so as to be inclined with respect to the longitudinal direction of the retainer. and a contact arm that feeds back the amount of movement of the retainer to the valve unit.