JPH08219247A - Toroidal type continuously variable transmission - Google Patents

Abstract

PURPOSE: To provide a structure capable of transmitting a large power without increasing the dimensions in the axial direction or the weight. CONSTITUTION: Rotation of an input shaft 42 is transmitted from an input part driving gear 45 to a plurality of input part driven gears 46, 46. The respective input part driven gears 46, 46 drive transmission units 44, 44 which are double cavity and toroidal type continuously variable transmissions. The output of the respective transmission sits 44, 44 is collected to one output part driven gear 47 from a plurality of output part driving gears 48, 48, and taken out from an output shaft 43. The overall length is suppressed by providing a plurality of transmission units 44, 44 in parallel to facilitate the securement of the rigidity of a easing or a bearing part.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION The toroidal type continuously variable transmission according to the present invention is used as a transmission for large vehicles such as buses and trucks.

[0002]

2. Description of the Related Art As a transmission for an automobile, the use of a toroidal type continuously variable transmission as schematically shown in FIGS. This toroidal type continuously variable transmission supports an input side disk 2 concentrically with an input shaft 1 rotatably supported inside a housing (not shown), and an end of an output shaft 3 also rotatably supported with respect to the housing. The output side disk 4 is fixed to the section. An inner surface of the housing in which the toroidal type continuously variable transmission is housed or a support bracket provided in the housing swings around a pivot shaft in a twisted position with respect to the input shaft 1 and the output shaft 3. Trunnions 5 and 5 are provided.

Each trunnion 5, 5 is made of a metal material having sufficient rigidity, and has the pivots on the outer surfaces of both ends. Power rollers 7, 7 are rotatably supported around displacement shafts 6, 6 provided at the center of each trunnion 5, 5. The power rollers 7, 7 are sandwiched between the input side and output side disks 2, 4.

On both axial surfaces of the input side and output side disks 2 and 4, which are opposed to each other, the cross sections are arc-shaped toroidal curved surfaces centered on a point on the center line of the pivot. An input side concave surface 2a and an output side concave surface 4a are formed. Then, the peripheral surfaces 7a, 7a of the power rollers 7, 7 formed on the convex surface of the rotating arc surface are replaced with the concave surface 2 on the input side.
a and the output-side concave surface 4a.

A loading cam type pressing device 8 is provided between the input shaft 1 and the input side disc 2, and the input side disc 2 is pressed toward the output side disc 4 by the pressing device 8. . The pressing device 8 includes a cam plate 9 that rotates together with the input shaft 1, and a plurality of (for example, four) rollers 11 and 11 held by a holder 10. A first cam surface 12, which is an uneven surface extending in the circumferential direction, is formed on one side surface (the right side surface in FIGS. 5 and 6) of the cam plate 9, and the outer surface (FIG. 5) of the input side disk 2 is formed. ~
The left side surface of 6 also has a second cam surface 1 having a similar shape.
3 is formed. The plurality of rollers 11,
11 is rotatable about an axis in the radial direction with respect to the center of the input shaft 1. Incidentally, the input side disk 2
Is supported on the input shaft 1 so as to be slidable in the axial direction (left and right directions in FIGS. 5 and 6) and rotatable in the rotational direction.

When the cam plate 9 rotates in accordance with the rotation of the input shaft 1 and a rotational phase difference is generated with respect to the input side disk 2, a plurality of rollers 11, 11 are moved by the first cam surface 12 and the second cam surface. The cam plate 9 and the input side disk 2 are moved away from each other by riding on the cam surface 13 of the. Since the cam plate 9 is supported by the input shaft 1 supported by the bearing by the housing so as not to move in the axial direction, the input side disk 2 is pushed toward the power rollers 7, 7, 7, 7 are pushed toward the output side disk 4. On the other hand, the output side disk 4 is rotatably supported together with the output shaft 3 with respect to the transmission case and does not move in the axial direction. Therefore, the power rollers 7 and 7 are connected to the input side disc 2 and the output side disc 4 respectively.
Pressed between and. By this pressing, the power roller 7,
7, peripheral surfaces 7a, 7a and input-side and output-side biconcave surfaces 2a, 4a
A pressing force is generated between the output side disc 4 and the input side disc 2 through the power rollers 7 and 7 without the rotation of the input side disc 2 slipping.
And the output shaft 3 fixed to the output side disk 4 rotates.

When changing the rotational speed ratio (gear ratio) between the input shaft 1 and the output shaft 3 and first decelerating between the input shaft 1 and the output shaft 3, as shown in FIG. The trunnions 5 and 5 are swung about the pivot, and the peripheral surfaces 7a and 7a of the power rollers 7 and 7 are brought into contact with the central portion of the input concave surface 2a and the outer peripheral portion of the output concave surface 4a, respectively. Similarly, the displacement axes 6, 6 are tilted. On the contrary, when increasing the speed, the trunnion 5, as shown in FIG.
5, the power roller 7, 7 of the peripheral surface 7a, 7a
Of the input side concave surface 2a and the output side concave surface 4a.
The displacement shafts 6, 6 are tilted so that they are brought into contact with the central portions of the displacement shafts 6, 6, respectively. By setting the inclination angles of the displacement shafts 6, 6 in the middle between FIG. 5 and FIG. 6, an intermediate gear ratio can be obtained between the input shaft 1 and the output shaft 3.

The basic structure and operation of the toroidal type continuously variable transmission are as described above, and such a toroidal type continuously variable transmission is used as a transmission for an automobile having a large output engine. In this case, two input-side disks 2 and two output-side disks 4 are provided to secure the power that can be transmitted, and these two input-side disks 2 and output-side disks 4 are arranged in the power transmission direction. On the other hand, it is conventionally known that they are arranged in parallel with each other, as described in, for example, Japanese Patent Application Laid-Open No. 4-69439. Figure 7
Shows the structure described in this publication.

In this conventional structure, the housing 14
The input side rotating shaft 15 is supported inside the shaft so as to be rotatable only. The input side rotation shaft 15 is composed of a front half portion 15a coupled to the output side rotation shaft of the clutch and the like, and a rear half portion 15b which is slightly rotatable with respect to the front half portion 15a. Among these, a pair of input side disks 2 and 2 corresponding to the first disk are provided near both ends in the axial direction (left and right direction in FIG. 7) of the rear half portion 15b corresponding to the rotating shaft described in the claims.
In a state where the respective input-side concave surfaces 2a, 2a corresponding to the first concave surface are opposed to each other, the ball spline 16,
It is supported through 16. In addition, recesses 20 and 20 are formed in the center of the back surface (the surface on the axially opposite side of the input side concave surfaces 2a and 2a) of each of the input side disks 2 and 2.

Of these recesses 20, 20,
A seat plate 29 and disc springs 30 and 30 are provided in series between the inner surface of the recess 20 on the rear end side (right side in FIG. 7) and the loading nut 28. A thrust needle bearing 31 and a disc spring 30 are provided between the inner surface of the recess 20 on the front end side (left side in FIG. 7) and the inner peripheral portion of one surface (right side surface in FIG. 7) of the cam plate 9 described later. , 30 are provided in series with each other. The thrust needle bearing 31 compensates the relative rotation between the cam plate 9 and the input side disc 2 on the front end side.
Further, the disc springs 30, 30 apply a preload to the input side disks 2, 2 toward the output side disks 4, 4 described below.

Around the middle portion of the latter half portion 15b, a pair of output side disks 4 and 4 corresponding to the second disk, and output side concave surfaces 4a and 4a corresponding to the second concave surface and the respective input sides. With the concave surfaces 2a, 2a facing each other, the input side rotary shaft 15 is freely supported for rotation.
Further, a plurality of power rollers 7, 7 rotatably supported by a plurality of trunnions 5, 5 via a displacement shaft 6 (FIGS. 5-6).
Is sandwiched between the input-side and output-side concave surfaces 2a, 4a. The power rollers 7, 7 are synchronously tilted so that the speed ratios between the input side disks 2, 2 and the output side disks 4, 4 match.

An output side rotary shaft 17 is provided inside the housing 14 on the side opposite to the front half part 15a, concentrically with the rear half part 15b of the input side rotary shaft 15, and independent of the latter half part 15b. And it is rotatably supported. Then, a rotation transmission means as described below is provided between the output side rotary shaft 17 and the pair of output side discs 4 and 4 to rotate the both output side discs 4 and 4 by the output side rotary shaft. 17 can be transmitted freely.

A partition wall 18 is provided inside the housing 14 between the pair of output disks 4, 4. Then, a cylindrical sleeve 21 is provided inside the through hole 19 provided in the partition wall 18 to form a pair of rolling bearings 27,
It is supported by 27. The pair of output disks 4, 4 are spline-engaged with both ends of the sleeve 21. That is, the male spline grooves formed on the outer peripheral surfaces of both ends of the sleeve 21 and the output side disks 4, 4 are formed.
And the female spline groove formed on the inner peripheral surface thereof are meshed with each other. Further, the partition wall 18 is formed at the intermediate portion of the sleeve 21.
A first gear 22 is fixed to the inner portion of the. Furthermore, the inner peripheral surface of a part of each of the output side disks 4, 4 protruding from the sleeve 21 and the input side rotating shaft 15
Roller bearings 32, 32 are provided between the outer peripheral surface and the outer peripheral surface, respectively. The roller bearings 32, 32 allow relative rotation between the output disks 4, 4 and the input rotary shaft 15 and relative displacement in the axial direction.

On the other hand, inside the housing 14, a transmission shaft 23 is rotatably supported in parallel with the input side rotary shaft 15 and the output side rotary shaft 17. Then, the second gear 24 fixed to one end (the left end in FIG. 7) of the transmission shaft 23.
And the first gear 22 are directly meshed with each other, and the transmission shaft 2
A third gear 25 fixed to the other end of 3 (the right end in FIG. 7),
The fourth gear 26 fixed to the end of the output side rotating shaft 17
And are meshed with each other via an idle gear (not shown). By such a rotation transmission means, the output side rotation shaft 1
7 rotates in the direction opposite to the output disks 4, 4 as the pair of output disks 4, 4 rotate.

Further, a loading cam type pressing device 8 is provided between the front half portion 15a and one (left side in FIG. 7) input side disk 2. And this pressing device 8
As a result, the one input side disk 2 can be axially pressed toward the output side disk 4 facing the one input side disk 2 while rotating the one input side disk 2 as the front half portion 15a rotates. For this reason, the engaging portion 33a formed on the outer peripheral surface of the rear end portion of the front half portion 15a and the engaging portion 33b formed on the back surface of the cam plate 9 constituting the pressing device 8 are engaged with each other. Further, a thrust ball bearing 34 is provided between the cam plate 9 and the flange portion 35 formed on the outer peripheral surface of the front end portion of the rear half portion 15b. The thrust ball bearing 34 bears the thrust load acting on the cam plate 9 when the pressing device 8 is operated, and also supports the cam plate 9 and the rear half portion 15.
Allow relative displacement with respect to b in the direction of rotation.

During operation of the toroidal type continuously variable transmission shown in FIG. 7, which is constructed as described above, the pair of input side disks 2 and 2 simultaneously rotate as the input side rotating shaft 15 rotates, This rotation is applied to the pair of output disks 4 and 4 at the same time.
In addition, they are transmitted at the same gear ratio, and are transmitted to the output side rotation shaft 17 by the rotation transmission means described above and taken out. At this time, the transmission of the rotational force is performed separately in two parallel systems, so that a large amount of power (torque) can be transmitted. Also, during operation, due to the operation of the pressing device 8,
The space between the pair of input side disks 2, 2 tends to be narrowed. As a result, these input side disks 2,
The input concave surfaces 2a, 2a and the output concave surfaces 4a, 4a of the output disks 4, 4 and the peripheral surfaces 7a, 7a of the power rollers 7, 7 are in strong contact with each other to efficiently transmit power. Will be performed.

As shown in FIG. 7, a so-called double-cavity toroidal type in which two input side disks 2 and 2 and two output side disks 4 and 4 are provided in parallel with each other in the power transmission direction. In the case of a continuously variable transmission, a larger amount of power can be transmitted as compared with a single cavity type toroidal type continuously variable transmission as shown in FIGS. However, it is not sufficient to configure a transmission for a large vehicle such as a bus or a large truck equipped with an engine having a large output (especially torque). As a structure in which the toroidal type continuously variable transmission is configured as a transmission for such a large automobile, for example, one described in US Pat. No. 5,308,297 is known. FIG. 8 shows the toroidal type continuously variable transmission described in this specification.

The rotations of the input side disks 38a and 38b which rotate together with the input shaft 37 which is rotationally driven by the engine 36 are transmitted to the output side disks 39 and 39 through the power rollers 7 and 7, respectively. Further, the rotation of the output side disks 39, 39 is transmitted to the output shaft 41 via the chains 40, 40. In the case of the toroidal type continuously variable transmission shown in FIG. 8, since the power transmission is divided into six systems, it can be used as a transmission for a large-sized automobile having a large output.

[0019]

In the toroidal type continuously variable transmission having the structure shown in FIG. 8, input rollers 38a, 38b and output disks 39, 3 are provided by power rollers 7, 7.
There are many units (6 in FIG.
Since it is provided, it is possible to transmit a large output,
Practical application is difficult because of the following points.

First, the input side disks 38a, 38
Since b and the output side disks 39, 39 are provided on one input shaft 37, the total length of the input shaft 37 and the output shaft 41 that receives power from the input shaft 37 becomes large. Therefore, the shafts 37, 41 and the disks 38a,
The overall length of the casing for supporting 38b, 39 also becomes long, and it becomes difficult to support the shafts 37, 41 and the disks 38a, 38b, 39 with sufficient rigidity inside the casing. If it can be supported with sufficient rigidity,
When a casing that can also secure its own rigidity is configured, the weight of this casing is considerably increased.

Secondly, although the total length of the input shaft 37 and the output shaft 41 becomes long, it is difficult to support the intermediate portion of the input shaft 37 by a bearing, so that the distance between the bearings becomes considerably long. Therefore, when the toroidal type continuously variable transmission is in operation, the input shaft 37 is likely to cause whirling motion. Therefore, in order to ensure the reliability and durability of the input shaft 37, the toroidal type continuously variable transmission cannot be operated at high speed.

Thirdly, since the entire length of the toroidal type continuously variable transmission including the casing becomes large, the mountability on a vehicle deteriorates. Although it is a large vehicle, the space for mounting the transmission is limited, and the deterioration of the mountability is not preferable. In particular, in the case of a structure in which the rear wheels are driven by an engine mounted in the rear of the vehicle body, such as a large-sized bus, it is extremely difficult to mount a transmission with a long overall length. Is not preferable because it narrows. The toroidal-type continuously variable transmission of the present invention was invented to eliminate all of these disadvantages.

[0023]

The toroidal type continuously variable transmission of the present invention satisfies the following requirements. One input shaft, one output shaft axially separated from the input shaft, and a plurality of transmission units provided between the input shaft and the output shaft are provided. . Each of the plurality of transmission units has a rotation shaft,
Each one side in the axial direction is the first concave surface with an arc cross section,
A pair of first disks, which are rotatably supported together with the rotating shaft, at both axial end portions of the rotating shaft with the first concave surfaces facing each other, and around an intermediate portion of the rotating shaft. A cylindrical sleeve supported so as to be freely rotatable about the rotation axis and displaced in the axial direction, and one axial side of each of the sleeves is a second concave surface having an arc-shaped cross section, and each second concave surface and each of the above-mentioned first concave surfaces. A pair of second disks rotatably supported together with the sleeve at both axial ends of the sleeve in a state where the one concave surface is opposed to the sleeve, and rocks about a pivot shaft in a twisted position with respect to the rotation shaft. A plurality of moving trunnions, the circumferential surface of which is a convex surface of a rotating arc surface, is rotatably supported by a displacement shaft supported by each trunnion, and is sandwiched between the first and second concave surfaces. Multiple power rollers and input members A loading cam-type pressing device that brings the first and second discs with the first and second concave surfaces facing each other along the axial direction and brings them closer to each other along the axial direction. The rotary shaft and the sleeve are attached to one of them, and the other of the rotary shaft and the sleeve functions as an output member of each transmission unit. An input part drive gear fixed to the input shaft and an input part driven gear fixed to the input member of the pressing device of each transmission unit concentrically with or integrally with the input member mesh with each other. . An output driven gear fixed to the output shaft and an output driving gear fixed to the output member of each transmission unit concentrically with the output member mesh with each other.

[0024]

When the toroidal type continuously variable transmission of the present invention constructed as described above is used, the power transmitted to the input shaft is transmitted through the input drive gear and the input driven gear to each transmission unit. Is transmitted to the input member of the pressing device. Then, the plurality of transmission units are operated by the pressing device of each transmission unit to form a pair of first disks that rotate together with the rotating shaft, and a pair of second disks that are respectively supported on both ends of the sleeve. Power is transmitted between them. The action at the time of this power transmission and the action at the time of changing the rotational speed ratio between the first disc and the second disc are the same as in the case of the conventional toroidal type continuously variable transmission described above.
It should be noted that all the trunnions incorporated in each transmission unit oscillate in synchronism so that all the first and second discs have the same gear ratio.

Particularly, in the case of the toroidal type continuously variable transmission of the present invention, a plurality of transmission units each having two first disks and two second disks are arranged in parallel with each other. By increasing the number of power transmission paths, it becomes possible to transmit a large amount of power, and the total length of the toroidal type continuously variable transmission does not become too long.

[0026]

1 and 2 show a first embodiment of the present invention. A feature of the present invention is that the combination and arrangement of the constituent members are devised so as to increase the power that can be transmitted while suppressing the total length. The details such as the shapes of the constituent members are the same as those of the conventionally known toroidal type continuously variable transmission as shown in FIGS. Therefore,
With respect to the same parts, overlapping description will be omitted or simplified, and hereinafter, the characteristic part of the present invention will be mainly described. Further, for simplification, the trunnion 5 and the power roller 7 are shown in FIG.
(See FIGS. 5 to 6) are omitted.

The input shaft 42 is rotatably supported inside a housing (not shown), and is rotationally driven in a predetermined direction via a starting mechanism such as a torque converter and a rotation direction switching mechanism such as a planetary gear mechanism. It The output shaft 43 is also concentric with the input shaft 42 inside the housing,
It is rotatably supported and drives the wheels through a differential gear (not shown). Two sets of transmission units 4 are provided between the input shaft 42 and the output shaft 43.
4, 44 are provided so that the power can be transmitted from the input shaft 42 to the output shaft 43, and the rotational speed ratio between the shafts 42, 43 can be adjusted.

Each of the two sets of transmission units 44, 44 is constructed in the same manner as the double cavity type toroidal type continuously variable transmission shown in FIG. That is, at both end portions in the axial direction (the left-right direction of FIGS. 1 and 7) of the input side rotary shaft 15 (FIG. 7, the latter half portion 15b of the structure in FIG. 7) corresponding to the rotary shaft described in the claims. , A pair of input side disks 2 and 2 each corresponding to the first disk are rotatably supported together with the input side rotating shaft 15. Each of the pair of input side disks 2 and 2 has one axial side surface which is an input side concave surface 2a having a circular arc-shaped cross section corresponding to the first concave surface. Then, the pair of input side disks 2 and 2 are connected to the input side rotating shaft 15
Further, the input concave surfaces 2a, 2a are supported in a state of being opposed to each other.

A cylindrical sleeve 21 is supported around the intermediate portion of the input-side rotary shaft 15 so as to be freely rotatable and axially displaced with respect to the input-side rotary shaft 15. Then, the output side disks 4 and 4, which are second disks, are supported on both axial ends of the sleeve 21, respectively. The output side discs 4 and 4 have one axial side surfaces which are output side concave surfaces 4a and 4a having an arc-shaped cross section, which correspond to the second concave surfaces, respectively. The output-side disks 4 and 4 are supported by the sleeve 21 in a state where the output-side concave surfaces 4a and 4a and the input-side concave surfaces 2a and 2a face each other. These output side disks 4, 4
Are rotatable with the sleeve 21.

The displacement shafts 6 and 6 (FIGS. 5 to 6) supported by a plurality of trunnions 5 and 5 swinging around a pivot shaft in a twisted position with respect to the input side rotary shaft 15 are respectively provided. The power rollers 7 and 7 (FIGS. 5 to 6) whose peripheral surfaces 7a and 7a are convex surfaces having a rotating arc surface are rotatably supported. The power rollers 7, 7 are sandwiched between the input-side and output-side concave surfaces 2a, 4a.

Further, the second cam surface 13 formed on the outer side surface (left side surface in FIG. 1) of the input side disk 2 near the input shaft 42 (left side in FIG. 1) and one surface of the cam plate 9 (FIG. 1). A plurality of rollers 11, 11 are provided between the input side disc 2 near the input shaft 42 and the output side disc 4 facing the input side disc 2. A loading cam type pressing device 8 that presses in the axial direction is configured.

The rear end of the input shaft 42 (right end in FIG. 1)
The input section drive gear 45 is fixed concentrically with the input shaft 42. Also, the cam plate 9, which is an input member of the pressing devices 8, 8 constituting the transmission unit 44, 44,
On the other surface (left surface in FIG. 1) of 9, the input unit driven gears 46, 46 are provided.
Are fixed concentrically with the respective cam plates 9, 9. If the transmission units 44, 44 of the same size are used, it is preferable that the input driven gears 46, 46 have the same number of teeth. The input driven gears 46, 46 and the input drive gear 45 are in mesh with each other.

On the other hand, an output driven gear 47 is fixed to the front end of the output shaft 43 (left end in FIG. 1) concentrically with the output shaft 43. Further, the transmission units 44, 4 described above
4, the output portion drive gears 48, 48 are provided on the outer peripheral surfaces of the intermediate portions of the sleeves 21, 21, respectively.
It is fixed concentrically with 1. Output gears 48, 48
It is preferable that the numbers of teeth are the same when the transmission units 44, 44 having the same size are used. The output drive gears 48, 48 and the output driven gear 47 are in mesh with each other.
The ratio of the number of teeth of the input driven gears 46, 46 fixed to the input side end of each transmission unit 44, 44 to the number of teeth of the output driven gears 48, 48 fixed at the output side end is: It is a necessary condition that the transmission units 44, 44 are matched. As long as this requirement is satisfied, the sizes of the gears 46 and 48 can be selected in consideration of the mountability in the vehicle and the like.

When the toroidal type continuously variable transmission of the present invention constructed as described above is used, the power transmitted to the input shaft 42 is from one input drive gear 45 to two input drive gears 46. , 46, and transmitted to each transmission unit 44, 4
The cam plates 9 and 9 constituting the pressing device 8 of 4 are rotated. The transmission units 44, 44 are actuated by the pressing devices 8, 8 to form a pair of input-side disks 2, 2 rotating with the input-side rotating shaft 15, and the transmission units 44, 44 respectively on both ends of the sleeves 21, 21. Power is transmitted between the pair of output side disks 4 and 4 which are supported. The power transmitted to the output side disks 4 and 4 by the transmission units 44 and 44 is output from the output drive gears 48 and 48 fixed to the outer peripheral surfaces of the intermediate portions of the sleeves 21 and 21 as one output. It is transmitted to the partial driven gear 47 and taken out from one output shaft 43.

Particularly, in the case of the toroidal type continuously variable transmission of the present invention, each of the two input side disks 2 and 2 is provided.
And a transmission unit 4 having an output side disk 4, 4.
Since four and 44 are arranged in parallel with each other, it is possible to increase the power transmission path and transmit a large power.
For example, in the case of a structure in which two power rollers 7 and 7 are provided between the input-side disk 2 and the output-side disk 4 that face each other, three power rollers 7 and 7 are used, and three power rollers 7 and 7 are also used. In the case of the structure in which the respective power rollers 7, 7 are provided, the power is transmitted via the 12 power rollers 7, 7.

In order to ensure the durability of the toroidal type continuously variable transmission, an excessive contact portion between the peripheral surfaces 7a, 7a of the power rollers 7, 7 and the input-side and output-side biconcave surfaces 2a, 4a is excessive. In order to prevent the stress from being applied, it is necessary to arrange the plurality of power rollers 7, 7 in parallel with each other in the power transmission direction in order to suppress the power transmitted through each contact portion. In the case of the toroidal type continuously variable transmission of the present invention, since a large number of power rollers 7, 7 are arranged in parallel with each other in the power transmission direction as described above, a large durability is ensured while ensuring sufficient durability. Power can be transmitted freely.

In addition, the total length of the toroidal type continuously variable transmission does not become undesirably long, despite the large number of power rollers 7, 7. That is, the two transmission units 44, 4
4 are arranged in parallel to each other in the axial direction, all the input side and output side discs 3 as shown in FIG.
The total length is not bulky as in the case where 8a, 38b and 39 are axially arranged in series with each other. Therefore, each shaft 42, 4
It is possible to shorten the total length of the casing for supporting the trunnions that support the disks 3, 4 and the disks 2, 4, and to support the shafts 42, 43, 15 and the trunnions inside the casing with sufficient rigidity. Can be done easily. Moreover, the weight of this casing does not increase.

Further, since the total length of each of the shafts 42, 43, 15 does not become extremely long, the distance between the bearings does not become excessively long, and the input shaft 42 is operated during the operation of the toroidal type continuously variable transmission. , 43, 15 are less likely to cause whirling motion. Therefore, it becomes possible to operate the toroidal type continuously variable transmission at high speed while ensuring the reliability and durability of each of the shafts 42, 43, 15. Furthermore, since the entire length of the toroidal type continuously variable transmission including the above casing can be suppressed while enabling transmission of a large amount of power, the mountability on a vehicle is improved.

Next, FIG. 3 shows a second embodiment of the present invention. In the first embodiment described above, two sets of transmission units 44 and 44 (FIG. 1) were provided between the input shaft 42 and the output shaft 43, whereas in the case of this embodiment, three sets are provided. The transmission unit is installed. Therefore, in this embodiment,
Three input section driven gears 46, 46 are meshed with an input section drive gear 45 fixed to the rear end of the input shaft 42 (FIG. 1), and these three input section driven gears 46, 46 are used to set the above three sets. It is designed to drive the transmission unit of. Of course, three output unit drive gears are also provided. In the case of the present embodiment, as the number of transmission units is increased, larger power can be transmitted. Further, when the powers to be transmitted are the same, the size of the transmission unit can be reduced to reduce the axial dimension. The transmission units need not necessarily be arranged at equal pitches in the circumferential direction. Other configurations and operations are similar to those of the first embodiment described above. The transmission unit is 4
More than one can be provided.

Next, FIG. 4 shows a third embodiment of the present invention. In this embodiment, as the plurality of transmission units, the one having the structure described in Japanese Patent Application Laid-Open No. 5-26316 is used. Therefore, in this embodiment, each transmission unit 44
Output side rotary shafts 49, 49 corresponding to the rotary shafts described in the claims are provided on a and 44a. Then, output-side disks 4, 4 corresponding to the first disks are provided at both ends of the output-side rotating shafts 49, 49, respectively.
It is rotatably supported along with the shafts 9 and 49 and is supported so as not to be displaced in the axial direction. In addition, output drive gears 48, 4 fixed to the rear ends (right ends in FIG. 4) of the output-side rotary shafts 49, 49.
8 and an output driven gear 47 fixed to the front end (left end in FIG. 4) of the output shaft 43.

On the other hand, around the intermediate portion of the output side rotary shafts 49, 49, at both ends of the sleeves 21, 21 which are rotatably supported with respect to the output side rotary shafts 49, 49, the second disk is provided. Corresponding to the input side disks 2 and 2. The input side disks 2 and 2 are supported by the sleeves 21 and 21 so as to be displaceable in the axial direction (horizontal direction in FIG. 4) with respect to the sleeves 21 and 21 and to be rotatable together with the sleeves 21 and 21. ing. or,
A cam plate 9 which is an input member of the loading cam type pressing device 8 is provided around the intermediate portion of the sleeves 21.
a and 9a are rotatably supported with respect to the respective sleeves 21 and 21. Each of these cam plates 9a, 9a has first cam surfaces 12, 12 on both sides. The roller 1 is provided between the first cam surfaces 12 and 12 and the second cam surfaces 13 and 13 formed on the back surface of the input side disks 2 and 2.
The pressing devices 8 and 8 are configured by providing the devices 1 and 11.

Teeth are formed on the outer peripheral edges of the cam plates 9a, 9a, which are the input members of the pressing devices 8, 8, and the cam plates 9a, 9a also function as input section driven gears. I am trying to do it. And each of these cam plates 9
The teeth of the outer peripheral edges of a and 9a are meshed with the input drive gear 45 fixed to the rear end of the input shaft 42 (the right end in FIG. 4).

In the case of this embodiment constructed as described above, when the cam plates 9a, 9a rotate in accordance with the rotation of the input shaft 42, a pair of pressing units are provided for each transmission unit 44a, 44a. By the action of the devices 8, 8, each sleeve 2
The distance between the input side disks 2 and 2 supported on both ends of the disks 1 and 21 increases. Then, these input side disks 2, 2
Between the input-side concave surfaces 2a, 2a (second concave surface) and the output-side concave surfaces 4a, 4a (first concave surface) of the output-side disks 4, 4 are narrowed, and the input-side disks 2, 2 and the output side are Power is transmitted between the disks 4 and 4. As a result of this power transmission, the power transmitted to the output side rotary shafts 49, 49 is then transmitted from the output section drive gears 48, 48 to the output section driven gear 47 and taken out from the output shaft 43. Also in the case of the present embodiment configured and operating as described above, the same effect as that of the above-described first embodiment can be obtained.

[0044]

Since the toroidal type continuously variable transmission of the present invention is constructed and operates as described above, it is possible to transmit a large amount of power, the length and weight do not increase, and a high rotational motion can be transmitted. It is possible to realize a new automotive transmission and contribute to the practical application of a toroidal type continuously variable transmission that can be mounted on a large vehicle.

[Brief description of drawings]

FIG. 1 is a schematic cross-sectional view of essential parts showing a first embodiment of the present invention.

FIG. 2 is a view of the input drive gear and the input driven gear taken out and viewed from the left side of FIG.

FIG. 3 is a view similar to FIG. 2, showing a second embodiment of the present invention.

FIG. 4 is a view similar to FIG. 1 showing the third embodiment.

FIG. 5 is a side view showing the basic structure of the toroidal-type continuously variable transmission in a state of maximum deceleration.

FIG. 6 is a side view showing the same state at the time of maximum acceleration.

FIG. 7 is a cross-sectional view showing an example of a specific structure of a conventionally known toroidal type continuously variable transmission.

FIG. 8 is a schematic cross-sectional view of a main part of a conventionally known toroidal-type continuously variable transmission capable of transmitting large power.

[Explanation of symbols]

 1 Input Shaft 2 Input Side Disc 2a Input Side Concave Surface 3 Output Shaft 4 Output Side Disc 4a Output Side Concave Surface 5 Trunnion 6 Displacement Shaft 7 Power Roller 7a Circumferential Surface 8 Pressing Device 9, 9a Cam Plate 10 Cage 11 Roller 12 First Cam surface 13 Second cam surface 14 Housing 15 Input side rotating shaft 15a Front half 15b Second half 16 Ball spline 17 Output side rotating shaft 18 Partition wall 19 Through hole 20 Recess 21 Sleeve 22 First gear 23 Transmission shaft 24 Second Gear 25 Third Gear 26 Fourth Gear 27 Rolling Bearing 28 Loading Nut 29 Seat Plate 30 Disc Spring 31 Thrust Needle Bearing 32 Roller Bearing 33a, 33b Engagement Part 34 Thrust Ball Bearing 35 Collar 36 Engine 37 Input Shaft 38a, 38b Input side disc 39 Output side disc 40 Chain 41 Output shaft 42 Input shaft 43 Output shaft 44, 44a Transmission unit 45 Input part drive gear 46 Input part driven gear 47 Output part driven gear 48 Output part drive gear 49 Output side rotating shaft

Claims (1)

[Claims] 1. A toroidal type continuously variable transmission satisfying the following requirements. One input shaft, one output shaft axially separated from the input shaft, and a plurality of transmission units provided between the input shaft and the output shaft are provided. . Each of the plurality of transmission units has a rotation shaft,
Each one side in the axial direction is the first concave surface with an arc cross section,
A pair of first disks, which are rotatably supported together with the rotating shaft, at both axial end portions of the rotating shaft with the first concave surfaces facing each other, and around an intermediate portion of the rotating shaft. A cylindrical sleeve supported so as to be freely rotatable about the rotation axis and displaced in the axial direction, and one axial side of each of the sleeves is a second concave surface having an arc-shaped cross section, and each second concave surface and each of the above-mentioned first concave surfaces. A pair of second disks rotatably supported together with the sleeve at both axial ends of the sleeve in a state where the one concave surface is opposed to the sleeve, and rocks about a pivot shaft in a twisted position with respect to the rotation shaft. A plurality of moving trunnions, the circumferential surface of which is a convex surface of a rotating arc surface, is rotatably supported by a displacement shaft supported by each trunnion, and is sandwiched between the first and second concave surfaces. Multiple power rollers and input members A loading cam-type pressing device that brings the first and second discs with the first and second concave surfaces facing each other along the axial direction and brings them closer to each other along the axial direction. The rotary shaft and the sleeve are attached to one of them, and the other of the rotary shaft and the sleeve functions as an output member of each transmission unit. An input drive gear fixed to the input shaft and an input driven gear fixed to or integrally formed with the input member of the pressing device of each transmission unit concentrically with the input member mesh with each other. . An output driven gear fixed to the output shaft and an output driving gear fixed to the output member of each transmission unit concentrically with the output member mesh with each other.