JPS622061A - Friction type continuously variable transmission - Google Patents

Abstract

PURPOSE:To well transmit output torque of a prime moving member, by rotating a rotary disc for use of an input at a speed almost equal to that of a rotary shaft of the prime moving member through an input shaft. CONSTITUTION:A transmission provides a rotary disc 21 for use of an output to be arranged in a position opposed to a rotary disc 20 for use of an input. While the transmission provides rollers 22 brought into contact with opposed surfaces of the both rotary discs 20, 21. Further the transmission, forming the roller 22 so as to enable its contact position to be changed, controls a rotary speed, transmitted to the rotary disc 21 for use of the output, to be changed. By this constitution, output torque of a prime moving member can be well transmitted.

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, and has a concave curved surface 4a similar to the rotary disk 3 for input. and a loading cam plate 6 rotatably provided on the output shaft 2 and connected to the input rotating disk 3 via a loading cam 5. , an input shaft 8 connected to the loading cam plate 6 via a deceleration mechanism 7, and on both sides of 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 that supplies working fluid to operate these pistons 14;
A cam 17 is provided between the bushing rod 16 of the 4-way valve 15 and one of the retainers 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 is configured.

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 presses the roller 9 against the output rotary disk 4 and also presses the input rotary disk 3.
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, the contact position A- with both rotary disks 3.4 before movement is shown in FIG.
A' is a position B − which is shifted from the center of rotation of the roller 9.
Move to B'. On the other hand, while this displacement of the contact position occurs, the loading cam 5 and the loading cam plate 6
Since the contact between the roller 9 and both rotating disks 3.4 is maintained by the action of , and the rotational force is continuously transmitted, at the contact position BB', the third
Frictional force as shown by arrow F in the figure acts on roller 9.

A component force F of this frictional force F in the direction of the rotation axis of both rotating disks 3.4 acts on the roller 9 in the same direction at each contact position, and as a result, the roller 9 moves 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. In addition, as the roller 9 moves toward the contact position before movement as described above with the tilting operation, the component force F1 decreases, and at the time when the component force FIh40 is reached, the desired tilting amount, that is, the shift amount is reached. can get.

Further, the amount of tilting of the roller 9 is fed back to the four-way valve 15 by the cam 17 as the amount of rotation of the retainer 11, and as described above, the operation of each piston 14 is stopped when the desired amount of tilting is obtained. 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 toric drive friction type continuously variable transmission, the maximum torque that can be transmitted between the output shaft 2 and the input rotating disk 3 is the maximum torque that can be transmitted between both rotating disks 3.4 and the roller 9. If the maximum torque, which is uniquely determined by the frictional force generated, is exceeded, the rotating disk 3.4 and the roller 9
Due to this, the rotating disk 3.4
Alternatively, the roller 9 may be fatally damaged, or the prime mover may be damaged in some cases. Furthermore, it is known that the output horsepower of a prime mover or transmission is determined by the product of torque and rotation of the output shaft. Since the rotation is firstly reduced by the speed reduction mechanism 7 and transmitted to the input rotating disk 3, the torque generated in the prime mover etc. is amplified and transmitted to the input rotating disk 3. However, as mentioned above, the maximum torque that can be transmitted by the toric-driven friction type continuously variable transmission is constant, and the rotation of the input rotary disk 3 is decelerated by the deceleration mechanism.
The problem is that the maximum horsepower that can be transmitted by the transmission is small, making it impossible to utilize the transmission effectively.

"Means for Solving the Problems" The present invention aims to provide a friction type continuously variable transmission that can effectively solve the problems in the conventional technology described above.
In particular, the friction-type continuously variable transmission includes an input shaft directly connected to a prime mover, an input rotating disk that is integrally rotatably attached to the input shaft, and an input rotating disk that faces the input rotating disk. an output rotary disk arranged and rotatably supported by the input shaft; and an output rotary disk that contacts opposing surfaces of the two rotary disks to output the rotation of the input rotary disk. a roller that changes the number of rotations transmitted to the output rotating disk by changing the contact position with each rotating disk, and a roller that is connected to the output rotating disk via a speed reduction mechanism. and an output shaft.

"Operation" The present invention is capable of transmitting the torque and rotation of the prime mover as directly as possible to the input rotating disk by attaching an input rotating disk to the input shaft directly connected to the prime mover and rotating the disk integrally. By rotating the input rotary disk in the same way as the prime mover, we can effectively utilize the characteristic that the maximum torque that can be transmitted in a toric drive transmission is constant, and maintain the output of the prime mover as much as possible while controlling the various components in the subsequent stages. This is what is transmitted to the device.

"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.
1 by contacting the opposing surfaces 20a and 21a of the rotary disks 20 and 21a to transmit the rotation of the input rotary disk 20 to the output rotary disk 21, and by changing the contact position with each of the rotary disks 20 and 21. A roller 22 that changes the number of rotations transmitted to the output rotating disk 21, and the output rotating disk 2.
1 and an output shaft 24 connected to the output shaft 24 via a speed reduction mechanism 23.

Next, to explain these details, the input shaft 1
9 has one end that penetrates a part of the casing C forming the outer shell of the transmission l and projects to the outside of the casing C, and the penetrating part and the other end of the casing C The casing C is rotatably supported by bearings 25 and 26 attached to the casing C.

Each opposing surface 2 of the input rotary disk 20.21
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 9 and rotatable around the input shaft. A loading cam plate 29 is connected to the side opposite to the side on which the surface 2Qa is formed via a loading cam 28, and the loading cam plate 29 is integrally connected to the input shaft 19. When the loading cam 28 and the loading cam plate 29 are rotated by the input shaft 19, the loading cam 28 and the loading cam plate 29 generate a wedge action between the input rotating disk 20 and the loading cam plate 29. The cam plate 29 and the input rotating circle Fi, 20 are connected, and the input rotating disk 20 is pressed toward the output rotating disk 21. On the other hand, the rotating disk 21 for output is
Its inner peripheral portion is supported by the input shaft 19 via a bearing 30, and its outer peripheral portion is supported by the casing C via a bearing 31. In addition, a rotary disk 21 for the output
A drive gear 32 is integrally provided on the side opposite to the side on which the facing surface 21a is formed, and the side mechanism 23 is constituted by a driven gear 33 that meshes with the drive gear 32. The driven gear 3
3 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.

The retainer 37 is provided for each of the rollers 22, and is provided on both sides of the input shaft 19 between the two rotating disks 2o, 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 moved to the casing C via a support pin 40. freely connected.

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 suppressing movement in the length direction of the
44 are arranged in series, and each of these pistons 41 to 44
are slidably fitted into hydraulic chambers 45 to 48 formed in the casing C.

As shown in FIG.
It is connected to a 4-way valve 5■ integrally provided in the casing C.

As shown in FIG. 4, the 4-way valve 51 has a housing made up of a part of the casing C, and an outer valve 52 that is slidably mounted on the casing C and slides concentrically inside the outer valve 52. The inner valve 53 is fitted freely.

The outer valve 52 is connected to each of the hydraulic chambers 45 to 45.
48 connected to two boats 54, 55 and an oil pump 59 via an oil filter 58 shown in FIG.
In this embodiment, the inner valve 53 operates as a spool that alternately connects each of the boats 54, 55 to the oil supply boat 6o. The diagonally located hydraulic chambers 45 and 47 and the hydraulic chambers 46 and 48 are set as a set and pressure oil is alternately supplied thereto.

Furthermore, the outer valve 52 includes a
2 in its length direction/(-61
is installed. 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 being engaged, connection with the outer valve 52 is established. Further, 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 operating lever 61 The outer valve 52 is moved.

The inner valve 53 projects outward from one end of the outer valve 52, and the projecting end has a groove 65 formed on the outer periphery of one of the retainers 37 at an angle with respect to its length. A pulling arm 67 is integrally provided which is slidably engaged with the retainer 66 and slides the inner valve 53 as the retainer 37 rotates.

The grooves 65 and 66 are formed in the retainer 3 as shown in FIG.
7 are formed so as to intersect at the middle when viewed from one side, and the cross-sectional shape is approximately V-shaped as shown in FIG. teeth,
Flat portions 65a, 6 along the direction of rotation of the retainer 37
6a is provided.

Further, the pulling arm 67 is formed of an elastic material into a U-shape (see FIG. 5), and contacts 68 are provided at both ends thereof to be engaged in the grooves 65 and 66 in a press-contact manner. As shown in FIG. 6, the contacts 68 are brought into contact with each other at two locations along the length of the retainer 37 while being pressed into the grooves 65 and 66. The pulling arm 67 includes a support rod 6 that is provided to pass through the inner valve 53 in the radial direction.
The inner valve 53 is attached to the inner valve 53 via the spring 70 and is interposed between the support rod 69 and the inner valve 53.
It is constantly being fired in the direction away from 3.

Therefore, when the retainer 37 is rotated due to the cooperation between the grooves 65 and 66 and the traction arm 67, the inner valve 53 is moved via the traction arm 67 along with the rotation, and the retainer 37 is rotated. Rotation amount is 4WAY valve 51
Hefeedback is now available.

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 input shaft 19 rotationally driven by the prime mover to the output shaft 24 while decelerating or increasing the speed.

That is, as the human power shaft 19 rotates, the loading cam plate 29 is rotated integrally. The rotation of the loading cam plate 29 causes the input rotary disk 20 to rotate in cooperation with the loading cam 28, and is pressed toward the output rotary disk 21, causing both rotary disks 20 to rotate. .21, the roller 22 located between the rollers 21 and 21 is held. Therefore, the roller 22 is connected to both rotating disks 20.
．． 2+, 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. .

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 characteristic of the transmission that the maximum torque that can be transmitted is constant is effectively utilized. Larger motor output can be transmitted with the same rotating disk and roller sizes as before.

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, the outer valve 52 of the 4-way valve 51 is moved relative to the casing C and the inner valve 53. By such movement of the outer valve 52, the oil supply port 60 formed in the outer valve 52 is connected to a set of hydraulic chambers 45.47 (46, 48), and pressure oil is supplied to these hydraulic chambers 45.47. is,
Along with this, the piston 41.43 fitted in the hydraulic chamber 45.47 and each retainer 37 to which the piston 41.43 is connected are moved as shown by arrows in FIG. Each retainer 37 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 inner valve 53 of the 4-way valve 51 is moved toward the outer valve due to the action of the grooves 65.66 formed in the retainer 37 and the pulling arm 67 that engages with the grooves 65.66. 52 to close the oil supply boat 60 and open the hydraulic chamber 4.
The supply of pressure oil to 5.47 is stopped, and accordingly, 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, between the inch valve 53 and the pulling arm 67, and between 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 V-shaped grooves 65 and 66 are brought into contact with the retainer 37 on both sides of the retainer 37 in the direction of movement, no rattling occurs between them, and thus the input by the control rod 64 is prevented. The amount of feedback from the retainer 37 is accurately transmitted, and the amount of shift is reliably controlled.

Furthermore, in this embodiment, 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 is attached to the retainer 37.
are installed in parallel near the 4-way valve 51, the overall shape becomes compact, the layout of the transmission 1 becomes easy, and the positional accuracy of the 4-way valve 51 with respect to the retainer 37 and the control rod 64 is improved. Also from this point of view, the aforementioned shift amount control is performed reliably.

Furthermore, by integrating the 4-way valve 51 with the casing C, the number of penetrating portions of the casing C can be reduced, thereby improving the liquid tightness inside the transmission l. 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 lubricating oil outside the transmission, there is a risk that the traction oil will not be as effective as described above. Improving fluid tightness is extremely effective in maintaining the functionality of the transmission.

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 an input shaft directly connected to the prime mover, and an input rotary disk that is integrally rotatably attached to the input shaft. , an output rotating disk disposed opposite to the input rotating disk and rotatably supported by the human power shaft; and an input rotating disk in contact with the opposing surfaces of both rotating disks. a roller that transmits the rotation of the rotating disk to the output rotating disk and changes the number of rotations transmitted to the output rotating disk by changing the contact position with each rotating disk; This device is characterized by having an output shaft connected to a rotating disk via a speed reduction mechanism, and has the following excellent effects.

■The rotation of the input rotating disk is made to rotate almost the same as the rotation of the prime mover via the input shaft, and therefore the rotational speed and torque of the prime mover are transmitted almost unchanged to the input rotating disk. , effectively utilizes the performance of the toric drive friction type continuously variable transmission, which has the characteristic that the maximum torque that can be transmitted is constant, to efficiently transmit the output torque of the prime mover, and also input the rotation speed of the prime mover. Because it can be added to the rotating disk of the conventional friction type continuously variable transmission, it is possible to generate a larger output of the prime mover with the same size of rotating disk and rollers as those installed on the output shaft. Can be communicated.

(2) Due to the effect (2) above, when a transmission is used in a prime mover having the same output, it is possible to downsize the transmission.

[Brief explanation of drawings]

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 pulling arm. It is an enlarged view of the main part showing. 18...Transmission, 19...Input shaft, 2
0... Rotating disk for input, 21... Rotating disk for output, 22... Roller, 23...
...Deceleration mechanism, 24...Output shaft, 28...
... Loading cam 1.29 ... Loading cam plate, 32 ... Drive gear, 3
3... Driven gear, 36... Eccentric shaft, 37... 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 rod, 65/66...
Groove, 65a/66a...Flat part, 67...
...Traction arm, 68...Contact element, 69...
・Support rod, 70...Spring, C...Casing.

Claims (1)

[Claims] an input shaft directly connected to the prime mover, an input rotating disk mounted to the input shaft so as to be integrally rotatable, and an input rotating disk disposed opposite to the input rotating disk and rotatably supported by the input shaft. 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 friction type comprising a roller that changes the number of rotations transmitted to the output rotating disk by changing its position, and an output shaft connected to the output rotating disk via a speed reduction mechanism. Continuously variable transmission.