JPH0645148U - Toroidal type continuously variable transmission - Google Patents

Abstract

(57) [Abstract] [Purpose] This toroidal type continuously variable transmission can obtain a predetermined gear ratio even when both toroidal transmission mechanisms do not work well in synchronization during gear shifting. [Structure] In this toroidal type continuously variable transmission, the input shaft 1 has bearings 45 and 46 with respect to supporting portions 47 and 49 of the casing.
Is supported so as to be rotatable but immovable in the axial direction, and the input shaft 1 is not displaced in the axial direction even when a thrust load is applied to the input shaft 1. On the other hand, the output disks 6 and 15 are axially immovably supported with respect to the input shaft 1 through thrust bearings 31 and 32. Therefore, the output disc 6,15
Is regulated in axial position with respect to the casing via the input shaft 1, so that the axial positions of the output disks 6, 15 and the power roller tilting shafts 9, 10, 18, 19 are controlled even during shifting. Is properly maintained and a predetermined gear ratio can be obtained.

Description

[Detailed description of the device]

[0001]

[Industrial applications]

 The present invention relates to a toroidal type continuously variable transmission applied to automobiles and the like, and more particularly to a double cavity type toroidal type continuously variable transmission in which two sets of toroidal transmission mechanisms are coaxially arranged.

[0002]

[Prior art]

 Generally, a toroidal type continuously variable transmission has a structure in which two sets of toroidal transmission mechanisms, which are an input disk, an output disk, and a power roller arranged between both disks, are coaxially arranged. The power transmission between the power roller and both discs depends on the shearing force of oil under high pressure, that is, the traction force (adhesive friction force), but in order to obtain a predetermined traction force, the contact point between the power roller and both discs Requires very large pressing force, that is, pressing force or pressure contact force.

This pressure contact force is generally generated by pressing both disks in the axial direction by a pressing means such as a loading cam. In the toroidal type continuously variable transmission, there are one in which the pressing means is provided only in one of the toroidal transmission mechanisms and the other in which the pressing means is provided in both the toroidal transmission mechanisms.

As an example of the former, there is a toroidal type continuously variable transmission disclosed in Japanese Laid-Open Patent Publication No. 1-216160. This toroidal type continuously variable transmission is a toroidal transmission mechanism having an input disk and an output disk for transmitting torque via a tiltable power roller. The two toroidal transmissions are connected to each other and are coaxially arranged. Two sets of pressing means for changing the pressure contact force of the power roller according to the magnitude of the input torque are provided in one of the toroidal transmissions. In the toroidal type continuously variable transmission, in which the pressing force of the pressing means is transmitted to the other toroidal speed change mechanism via the transmission member that can move in the axial direction and the pre-pressurizing means, is generated by the pressing means on one toroidal speed change mechanism side. In order to solve the problem of preventing frictional resistance from occurring in the preload means of the other toroidal transmission mechanism due to the phase shift that occurs, From the transfer member through the preload means the pressing force transduction pathway leading to the other of the torroid transmission mechanism is obtained by placing a rotatable thrust bearing. As a result, in this toroidal type continuously variable transmission, the thrust bearing absorbs the phase shift generated by the pressing means on the one toroidal transmission mechanism side, so that friction resistance is generated on the preload means of the other toroidal transmission mechanism. It is something that is prevented.

On the other hand, as an example of the latter, there is a toroidal type continuously variable transmission as shown in FIG. This toroidal type continuously variable transmission includes an input disc 4, an output disc 6 arranged facing the input disc 4, and tiltable power rollers 7 and 8 for transmitting torque from the input disc 4 to the output disc 6. The toroidal speed change mechanism 2 has an input disc 13, an output disc 15 arranged to face the input disc 13, and tiltable power rollers 16 and 17 for transmitting torque from the input disc 13 to the output disc 15. Two sets of toroidal speed change mechanism including the toroidal speed change mechanism 11 are arranged so as to face each other on the input shaft 1B, and the output disks 6 and 15 are connected by a connecting member 20 so as to be integrally rotatable. It is supported by bearings 22 and 23 that are rotatable with respect to the casing 24 and that regulate axial movement, and the input shaft 1A to the input disks 4 and 13 are supported. Power rollers 7 and 8 according to the magnitude of the input torque, 16, 17 of the pressing means 29, 30 for varying the contact pressure but on the respective toroidal transmission mechanism 2,11.

In this toroidal type continuously variable transmission, the engine torque is input to the first input shaft 1A via a torque converter (not shown). A second input shaft 1B is connected to the first input shaft 1A via a ball spline 1C so as to be movable in the axial direction. The first toroidal speed change mechanism 2 is rotatably attached to the second input shaft 1B via the radial bearing 3 and the first input disk 4 which is rotatably attached to the second input shaft 1B, and to the second input shaft 1B via the radial bearing 5. The first output disk 6 is arranged to face the first input disk 4, and the first power rollers 7 and 8 are arranged between the disks 4 and 6. The first power rollers 7 and 8 are provided so as to be tiltable with respect to the power roller tilt shafts 9 and 10 fixed to a casing (not shown). The first power rollers 7 and 8 themselves are disk-shaped and are configured to receive torque from the first input disk 4 to rotate and transmit the torque to the first output disk 6.

The second toroidal speed change mechanism 11 includes a second input disk 13 rotatably attached to the second input shaft 1B via a radial bearing 12 and a second input disk 1 rotatably attached to the second input shaft 1B via a radial bearing 14. And a second output disk 15 mounted to the second input disk 13 so as to face the second input disk 13, and second power rollers 16 and 17 arranged between the disks 13 and 15. The second power rollers 16 and 17 are respectively tiltably provided with respect to power roller tilting shafts 18 and 19 fixed to a casing (not shown). The second power rollers 16 and 17 themselves are disk-shaped, and are configured to receive torque from the second input disk 13 and rotate to transmit the torque to the second output disk 15.

The first output disk 6 and the second output disk 15 are connected to each other by a connecting member 20 and can rotate integrally. An output gear 21 is formed integrally with the connecting member 20, and the output gear 21 is supported by a support member 24 fixed to the casing via a pair of bearings 22 and 23 so as to be rotatable and immovable in the axial direction. ing. That is, both output disks 6 and 15 are configured so as not to move in the axial direction with respect to the casing. The output gear 21 meshes with the output gear 26 of the output shaft 25.

Flange portions 27 and 28 are provided at both ends of the second input shaft 1B, respectively. A loading cam 29 as a pressing means is provided between the flange portion 27 and the first input disk 4. A loading cam 30 as a pressing means is also provided between the flange portion 28 and the second input disk 13.

The toroidal type continuously variable transmission is configured as described above and operates as follows. When torque is input to the first input shaft 1A as the engine operates, the torque is transmitted from the first input shaft 1A to the second input shaft 1B via the ball spline 1S in which the ball 1C is fitted, Further, it is transmitted to the first input disk 4 via the flange portion 27 formed at one end of the second input shaft 1B and the loading cam 29, and the second portion is transmitted via the flange portion 28 and the loading cam 30 at the other end. Transmitted to the input disk 13, the first input disk 4 and the second input disk 13 rotate together.

The torque input to the first input disk 4 is transmitted to the first output disk 6 via the first power rollers 7 and 8. At this time, a speed change ratio corresponding to the tilt angles of the first power rollers 7 and 8 is continuously obtained between the first input disk 4 and the first output disk 6. On the other hand, the torque input to the second input disk 13 is transmitted to the second output disk 15 via the second power rollers 16 and 17. At this time, since the second power rollers 16 and 17 are configured to interlock with the first power rollers 7 and 8, the tilt angles of the second power rollers 7 and 8 are the same as those of the first power rollers. Thus, the same gear ratio can be continuously obtained. Then, the torque transmitted to the first output disc 6 and the second output disc 15 is transmitted to the output shaft 25 via the connecting member 20 and the output gear 21.

[0012]

[Problems to be solved by the device]

 By the way, in the toroidal type continuously variable transmission, in order to obtain a predetermined gear ratio, the axial positions of the power roller tilt shaft and the input / output disk must be fixed. That is, the toroidal center of the input / output disk must be on the power roller tilt axis in a plane that passes through the axes of the input disk and the output disk and intersects the power roller tilt axis directly. Therefore, in the conventional toroidal type continuously variable transmission shown in FIG. 3, the power rollers 7, 8, 16, 17 and the input / output disks 4, 6, 13, 15 are axially positioned as follows. ing. That is, the output disks 6 and 15 are positioned through the bearings 22 and 23 on the support member 24 integrated with the casing supporting the power roller tilting shafts 9, 10, 18, and 19, and the input disks 4, 13 are positioned. Is pressed against the power rollers 7, 8, 16, 17 by the loading cams 29, 30 to fix the position in the axial direction with respect to the output disks 6, 15 via the power rollers 7, 8, 16, 17. And indirectly positioned in the axial direction with respect to the power roller tilting shafts 9, 10, 18, and 19.

However, the input disks 4 and 13 may be displaced from the predetermined positions in the axial direction with respect to the power roller tilt shafts 9 and 10. That is, since the power roller is displaced in the tilt axis direction during gear shifting, the contact position between both disks and the power roller is displaced, and as a result, the input disks 4, 13 are displaced so as to approach the output disks 6, 15. To do. At this time, in the double-cavity type in which two sets of toroidal speed change mechanisms 2 and 11 are coaxially opposed to each other, if the two sets of toroidal speed change mechanisms are not perfectly synchronized, the input shaft will move axially during the speed change. It will be displaced. Therefore, conventionally, in order to absorb the axial displacement of the input shaft, the input shaft is divided into two parts on the prime mover side. For example, as shown in FIG. 3, the two input shafts 1A and 1B are connected to the ball spline. By adopting a structure such as 1S connection, the structure is such that only the rotation direction is connected and there is no axial restraint. For this reason, there is a drawback in that the number of parts that complicate the structure also increases.

Therefore, an object of the present invention is, in a toroidal type continuously variable transmission in which both toroidal transmission mechanisms are provided with pressing means, in the axial position of the output disc with respect to the power roller tilting shaft and the axial position of the input shaft. By controlling both of them, it is possible to obtain a predetermined gear ratio even if both toroidal speed change mechanisms do not synchronize well, and to provide a toroidal type continuously variable transmission with a simple input shaft structure and a small number of parts. That is.

[0015]

[Means for Solving the Problems]

 The present invention is configured as follows to achieve the above object. That is, according to the present invention, an input shaft that penetrates a casing, a pair of input disks that are rotatably supported by the input shaft, and a pair of input disks that are arranged to face each of the input disks and that are rotatable with respect to the input shaft. A pair of output discs supported by a pair of opposing output rollers, a pair of opposing power discs disposed between the input disc and the output disc and transmitting torque from the input disc to the output disc, and a pair of opposing output discs. A connecting member for integrally connecting the output disks, a pair of flange portions provided on the input shaft and the input disks, and acting on each of the input disks, depending on the magnitude of the input torque. In a toroidal type continuously variable transmission having a pressing means for changing the pressure contact force of a power roller, the toroidal type continuously variable transmission is rotatable with respect to the casing. And a pair of first bearings arranged between the flange portion of the input shaft and the casing for restricting axial movement, and arranged between the input shaft and the output disk, and with respect to the input shaft. The output disk is rotatably supported, and a pair of second bearings are provided for restricting axial movement of the input shaft by receiving a thrust load of the input shaft with respect to the output disk. Toroidal type continuously variable transmission

In this toroidal type continuously variable transmission, the second bearing is composed of a thrust bearing and a radial bearing.

Alternatively, in this toroidal type continuously variable transmission, the second bearing is configured by an angular bearing. Here, the angular bearing refers to a bearing such as an angular ball bearing or an angular cylindrical roller bearing, which can support angular contact with a nominal contact angle of not 0 °.

[0018]

[Action]

 Since the toroidal type continuously variable transmission according to the present invention is configured as described above, it operates as follows. First, in this toroidal type continuously variable transmission, it is assumed that, for example, a thrust load acts on the input shaft when two sets of toroidal transmission mechanisms are out of synchronization during gear shifting. However, since the input shaft is supported by the pair of first bearings so as to be rotatable and immovable in the axial direction with respect to the casing, the input shaft is not displaced in the axial direction. Instead, a reaction force of the thrust load acts on the input disc, and this force is transmitted to the output disc via the power roller. However, the output disc or the connecting member is supported by a pair of second bearings, which are thrust bearings that receive a thrust load with respect to the input shaft, so that the axial movement thereof is restricted, and the input shaft is supported by the casing as described above. Since it is supported immovably in the axial direction, the axial positions of the output disk and the power roller tilting shaft are properly maintained after all. Therefore, if this toroidal type continuously variable transmission is used, a predetermined gear ratio can be obtained even during gear shifting.

Alternatively, in this toroidal type continuously variable transmission, it is assumed that, for example, a thrust load acts on the input shaft when two sets of the toroidal transmission mechanisms are out of synchronization during shifting. However, since the input shaft is supported by the pair of first bearings so as to be rotatable and immovable in the axial direction with respect to the casing, the input shaft is not displaced in the axial direction. Instead, a thrust reaction force acts on the input disc, and this force is transmitted to the output disc via the power roller. However, the output disc or the connecting member is rotatably and immovably supported by the pair of second bearings, i.e., angular bearings, with respect to the input shaft, and the input shaft is supported by the casing as described above. Since it is supported by the first bearing so as to be rotatable and immovable in the axial direction, the axial positions of the output disc and the power roller tilting shaft can be properly maintained. Therefore, a predetermined gear ratio can be obtained even when the speed changes.

[0020]

【Example】

 An embodiment of the present invention will be described below with reference to the drawings. FIG. 1 is a sectional view showing an embodiment of the toroidal type continuously variable transmission according to the present invention. The structure of the toroidal type continuously variable transmission according to the present invention has basically the same structure as the toroidal type continuously variable transmission shown in FIG. 3, and has the same action as the reference numeral given in FIG. The same reference numerals are given to the parts.

This toroidal type continuously variable transmission is arranged so as to face the input shaft 1 and a pair of input disks 4 and 13 rotatably supported with respect to the input shaft 1 and input disks 4 and 13, respectively. A pair of output discs 6, 15 rotatably supported with respect to the shaft 1, and a tilting mechanism for transmitting torque from the input disc 4 to the output disc 6 arranged between a pair of opposing input discs 4 and 6. Possible power rollers 7, 8, tiltable power rollers 16, 17 arranged between a pair of equally facing input discs 13 and output discs 15 for transmitting torque from the input discs 13 to the output discs 15, Pressing means 29, 3 that act on each of the pair of input disks 4, 13 to change the pressure contact force of the power rollers 7, 8, 16, 17 according to the magnitude of the input torque. Has 0.

The toroidal type continuously variable transmission will be described in more detail. Engine torque is input to the input shaft 1 via a torque converter (not shown). The first toroidal speed change mechanism 2 is rotatably attached to the input shaft 1 via a radial bearing 3 and a first input disk 4 and to the input shaft 1 via a radial bearing 5 so as to rotate freely. It is composed of a first output disk 6 arranged to face the input disk 4, and a pair of first power rollers 7 and 8 arranged between the disks 4 and 6. The first power rollers 7 and 8 are provided so as to be tiltable with respect to power roller tilt shafts 9 and 10 fixed to a casing (not shown). The first power rollers 7 and 8 themselves are disk-shaped, and are configured to receive torque from the first input disk 4 to rotate and transmit the torque to the first output disk 6.

The second toroidal speed change mechanism 11 is rotatably attached to the input shaft 1 via a radial bearing 12 and a second input disk 13 and to the input shaft 1 via a radial bearing 14, respectively. It is composed of a second output disc 15 arranged to face the second input disc 13, and a pair of second power rollers 16 and 17 arranged between the two discs 13 and 15. The second power rollers 16 and 17 are provided so as to be tilted with respect to the power roller tilt shafts 18 and 19 fixed to a casing (not shown), respectively. The second power rollers 16 and 17 themselves are disk-shaped and are configured to receive torque from the second input disk 13 to rotate and transmit torque to the second output disk 15.

The first toroidal speed change mechanism 2 and the second toroidal speed change mechanism 11 are arranged on the input shaft 1 so that the output disks 6 and 15 of each other face each other. The first output disk 6 and the second output disk 15 are connected to each other by a connecting member 20 and can rotate integrally. An output gear 21 is integrally formed with the connecting member 20, and an output gear 26 of an output shaft 25 meshes with the output gear 21.

Flange portions 27 and 28 are formed at both ends of the input shaft 1, respectively. A loading cam 29 as a pressing means is provided between the flange portion 27 and the first input disk 4. Further, a loading cam 30 as a pressing means is provided between the flange portion 28 and the second input disk 13.

In the toroidal continuously variable transmission, the input shaft 1 is rotatably supported by supporting portions 47 and 49 (collectively referred to as a casing) provided in the casing, and the supporting portion 47 of the casing is provided. , 49, which are the first bearings and are supported so as to be immovable in the axial direction. The bearing 45 is fixed to a support portion 47 provided on the casing and a shoulder portion 48 formed on the input shaft 1. The bearing 46 is fixed to a support portion 49 provided on the casing and a shoulder portion 50 formed on the input shaft 1.

Further, the toroidal type continuously variable transmission has thrust bearings 31, 32 for supporting the output disks 6, 15 with respect to the input shaft 1 so as to be immovable in the axial direction. The thrust bearing 31 is arranged between the first input disk 4 and the first output disk 6 in the first toroidal speed change mechanism 2 and supports the input shaft 1 and the first output disk 6. An annular groove 33 is formed in the input shaft 1, and a circlip 34 is fitted in the annular groove 33. The thrust bearing 31 is in contact with the circlip 34 and the end surface of the first output disk 6, and the axial position is restricted. The thrust bearing 32, which supports the input shaft 1 and the second output disc 15, is arranged between the second input disc 13 and the second output disc 15 in the second toroidal speed change mechanism 11 like the thrust bearing 31. The circlip 36 fitted into the annular groove 35 formed in the input shaft 1 and the end surface of the second output disk 15 are brought into contact with each other to regulate the axial position.

The toroidal type continuously variable transmission is configured as described above and operates as follows. When torque is input to the input shaft 1 as the engine operates, the torque is transmitted to the first input disk 4 via the flange portion 27 formed at one end of the input shaft 1 and the loading cam 29. At the same time, it is transmitted to the second input disk 13 via the flange 28 and the loading cam 30 formed at the other end of the input shaft 1, so that the first disk 4 and the second input disk 13 rotate together.

The torque input to the first input disk 4 is transmitted to the first output disk 6 via the pair of first power rollers 7 and 8. On the other hand, the torque input to the second input disk 13 is transmitted to the second output disk 15 via the second power rollers 16 and 17. At this time, the first power rollers 7 and 8 move in conjunction with the second power rollers 16 and 17, and the speed change ratio according to the tilt angle of the power rollers is the same as that of the first input disk 4 and the first output disk 6. In between, and between the second input disk 13 and the second output disk 15, steplessly obtained. Then, the torque transmitted to the first output disc 6 and the second output disc 15 is transmitted to the connecting member 20 and further transmitted to the output shaft 25 via the output gears 21, 26.

When two sets of toroidal speed change mechanisms 2 and 11 are out of synchronization during speed change, it is assumed that, for example, a thrust force acts on the input shaft 1. However, since the input shaft 1 is rotatably supported by the bearings 45 and 46 with respect to the support portions 47 and 49 fixed to the casing and is immovable in the axial direction, the input shaft 1 is not displaced in the axial direction. Instead, a thrust reaction force acts on the input disk 4. For example, when a thrust reaction force acts from the first toroidal speed change mechanism 2 toward the second toroidal speed change mechanism 11, the thrust reaction force is applied to the first input disk 4 and the first power roller of the first toroidal speed change mechanism 2. 7, 8 and the first output disc 6, and is transmitted to the second output disc 15 of the second toroidal transmission mechanism 11 via the connecting member 20. However, the second output disk 15 is supported immovably in the axial direction with respect to the input shaft 1 by the thrust bearing 32 whose axial position is regulated by the circlip 36. As described above, the bearings 45 and 46 are supported rotatably and immovably in the axial direction with respect to the casing. Therefore, the axial positions of the first output disk 6 and the first power roller tilting shafts 9 and 10 are eventually determined. Will be properly maintained. On the contrary, when the thrust reaction force acts from the second toroidal speed change mechanism 11 toward the first toroidal speed change mechanism 2, the second output disk 15 and the second power roller tilting shaft 18 are similarly operated. , 19 are properly maintained in the axial position. As described above, since both output disks 6 and 15 are regulated in axial position with respect to the casing via the input shaft 1, axial positions with respect to the power roller tilting shafts 9, 10, 18, and 19 are set. Is properly maintained and a predetermined gear ratio can be obtained. In the first embodiment, the thrust bearings 31, 32 are provided as means for axially immovably supporting the output disks 6, 15 with respect to the input shaft 1, but the connecting member 20 is axially supported. It is the same even if it is provided as a means for immovably supporting.

Next, another embodiment of the toroidal type continuously variable transmission according to the present invention will be described. FIG. 2 is a sectional view showing another embodiment of the toroidal type continuously variable transmission according to the present invention. This toroidal type continuously variable transmission has basically the same structure as the toroidal type continuously variable transmission of the embodiment shown in FIG. One of the differences between the two is that the radial bearings 5 and 14 are abolished as bearings for supporting the output disks 6 and 15 on the input shaft 1, and angular bearings 37 and 38 are adopted instead. Is. Here, the angular bearing refers to a bearing such as an angular ball bearing or an angular cylindrical roller bearing, which can support an angular contact with a nominal contact angle of not 0 °. Another difference is that instead of supporting the output discs 6, 15 on the input shaft 1 by the thrust bearings 31, 32, the output discs 6, 15 (coupling member 20) are supported on the input shaft 1 by the angular bearings 37, 38. This is the point I supported. Other than that, the two have the same structure, and therefore the description of the parts having the same structure will be omitted.

The first output disk 6 has a recess 39 formed on the surface adjacent to the connecting member 20, and the angular bearing 37 is fitted in the recess 39 and is sandwiched by the end surface of the connecting member 20. A circlip 41 is fitted in the annular groove 40 formed in the input shaft 1, and the angular bearing 37 is sandwiched between the circlip 41 and one end surface of the connecting member 20. Similarly, the angular bearing 38 is also fitted into the recess 42 of the second output disk 15 and is sandwiched by the other end surface of the connecting member 20. Further, a circlip 44 is fitted in the annular groove 43 formed in the input shaft 1, and the angular bearing 38 is sandwiched between the circlip 44 and the other end surface of the connecting member 20.

When two sets of toroidal speed change mechanisms are out of synchronization during a speed change, for example, it is assumed that a thrust load acts on the input shaft 1. However, since the input shaft 1 is supported by bearings 45 and 46 with respect to the support portions 47 and 49 fixed to the casing, the input shaft 1 is supported in a state in which it cannot move in the axial direction, that is, the movement in the axial direction is restricted. Does not move axially. Instead, a thrust reaction force acts on the input disc. For example, when a reaction force of the thrust load acts from the first toroidal transmission mechanism 2 toward the second toroidal transmission mechanism 11, the reaction force is applied to the input disk 4 and the power roller 7 of the first toroidal transmission mechanism 2. , Is transmitted to the output disk 6, and further transmitted to the connecting member 20. However, the connecting member 20 is supported rotatably and immovably in the axial direction by the angular bearing 38 whose axial direction position is restricted by the circlip 44, and Since the input shaft 1 is rotatably supported by the bearings 45 and 46 with respect to the supporting members 47 and 49 of the casing and is immovable in the axial direction, in the end, the first output disk 6 and the first power roller tilting unit are rotated. The axial positions of the shafts 9 and 10 are properly maintained. On the contrary, when the reaction force of the thrust load acts in the direction from the second toroidal speed change mechanism 11 to the first toroidal speed change mechanism 2, the second output disk 15 and the second power roller tilt shaft 18 are similarly processed. , 19 are properly maintained in the axial position. In this way, since both output disks 6 and 15 are regulated in the axial position with respect to the casing via the input shaft 1, the shafts of the power roller tilting shafts 9, 10, 18 and 19 are aligned. The directional position is properly maintained and a predetermined gear ratio can be obtained. In the second embodiment, the angular bearings 37 and 38 are provided as means for supporting the connecting member 20 with respect to the input shaft 1 so as to be rotatable and immovable in the axial direction. Even if it is provided as a means for supporting rotatable but immovable in the axial direction, the same is true, but the former is preferable from the structural strength.

In the embodiment shown in FIG. 1, the first output disk 6 is rotatably supported on the input shaft 1 via the radial bearing 5, but in the embodiment shown in FIG. 2, the radial bearing is omitted, and the first output disk 6 is omitted. Instead, the single angular bearing 37 functions as both a radial bearing and a thrust bearing. Similarly, for the second output disk 15, one angular bearing 38 serves as both a radial bearing and a thrust bearing. Therefore, the toroidal type continuously variable transmission of the embodiment of FIG. 2 has an advantage that the number of parts can be further reduced as compared with the embodiment of FIG.

[0035]

[Effect of device]

 Since the toroidal type continuously variable transmission according to the present invention is configured as described above, it has the following effects. That is, according to this toroidal type continuously variable transmission, the position of the input shaft in the axial direction can be restricted with respect to the casing while the position of the output disk in the axial direction with respect to the tilt axis of the power roller is restricted. Even when the toroidal variable speed mechanism of the set is out of synchronization, a predetermined gear ratio can be obtained. Therefore, it is not necessary to divide the input shaft into two parts on the engine side as in the conventional case, the structure of the input shaft can be simplified, and the number of parts can be reduced.

Alternatively, since this toroidal type continuously variable transmission supports the output disc on the input shaft by the angular bearing, the radial bearing conventionally used to match the input shaft and the rotary shaft of the output disc is used. There is an advantage that it can be abolished and the number of parts can be further reduced compared to the conventional toroidal type continuously variable transmission.

[Brief description of drawings]

FIG. 1 is a sectional view showing an embodiment of a toroidal type continuously variable transmission according to the present invention.

FIG. 2 is a sectional view showing another embodiment of the toroidal type continuously variable transmission according to the present invention.

FIG. 3 is a sectional view showing a conventional toroidal type continuously variable transmission.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Input shaft 2 1st toroidal speed change mechanism 4 1st input disk 6 1st output disk 7,8 1st power roller 9,10 Power roller tilting shaft 11 2nd toroidal speed change mechanism 13 2nd input disk 15 2nd output disk 16, 17 Second power roller 18, 19 Power roller tilting shaft 20 Connecting member 27, 28 Flange portion 29, 30 Loading cam (pressing means) 31, 32 Thrust bearing 37, 38 Angular bearing (second bearing) 45, 46 Bearing (first bearing) 47,49 Supporting portion of casing (casing)

Claims (3)

[Scope of utility model registration request] 1. An input shaft penetrating a casing, a pair of input disks rotatably supported with respect to the input shaft, arranged to face each of the input disks and rotatable with respect to the input shaft. A pair of supported output discs, a tiltable power roller arranged between a pair of the input discs and the output discs facing each other and transmitting torque from the input discs to the output discs, a pair of the opposing ones. A coupling member that integrally couples the output discs, a pair of flanges provided on the input shaft and the input disc, and the power is applied to each of the input discs according to the magnitude of the input torque. In a toroidal type continuously variable transmission having a pressing means for changing the pressure contact force of a roller, the toroidal type continuously variable transmission is rotatable with respect to the casing and axially movable. And a pair of first bearings arranged between the flange portion of the input shaft and the casing, and arranged between the input shaft and the output disc to rotate the output disc with respect to the input shaft. A toroidal type continuously variable transmission, which is provided with a pair of second bearings that are freely supported and that restrict the axial movement of the input shaft by receiving the thrust load of the input shaft with respect to the output disk. . 2. The toroidal type continuously variable transmission according to claim 1, wherein the second bearing is composed of a thrust bearing and a radial bearing. 3. The toroidal type continuously variable transmission according to claim 1, wherein the second bearing is an angular bearing.