JPH11210773A - Bearing of double cavity type toroidal continuously variable transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a bearing of a double cavity type toroidal continuously variable transmission which enhances the strength of coupling between the bearing and a casing while reducing the number of part items for simplification of the processes of machining, assembly, and maintenance and for a reduction in weight of the entire transmission. SOLUTION: In a double cavity type toroidal continuously variable transmission having two toroidal transmission mechanisms, in which the two output disks of the toroidal transmission mechanisms are coupled back-to-back via an output gear shaft 4 which rotates integrally with an output gear 3, a bearing which is provided between the output disks 12, 23 and the output gear 3 to support loads applied to the output gear 3 along a thrust direction and a radial direction has outer rings each provided with a flange extending in the radial direction of a torque input shaft, with the outer edge of each flange directly secured to the casing 7 of the toroidal continuously variable transmission.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a double-cavity toroidal type continuously variable transmission used as, for example, a transmission of an automobile, which is installed between two output disks and one output gear to provide an output. The present invention relates to a bearing structure for supporting loads in a thrust direction and a radial direction applied to a gear.

[0002]

2. Description of the Related Art Toroidal-type continuously variable transmissions, which have been studied mainly as transmissions for automobiles, include an input disk and an output disk each having a concave section having an arc-shaped concave surface facing each other. A toroidal speed change mechanism having a structure combining a rotatable power roller sandwiched between two disks is provided. At this time, the input disk is locked and mounted so as to be integrally rotatable with respect to the torque input shaft and restricted from moving in the direction of the torque input shaft, while the output disk is mounted with respect to the torque input shaft. It is mounted opposite to the input disk so as to be relatively rotatable and restricted from moving away from the input disk.

In the above-described toroidal transmission, when the input disk rotates, the output disk rotates reversely via the power roller. Therefore, the rotational motion input to the torque input shaft is output as a rotational motion in the opposite direction. It is transmitted to the disk and taken out. At this time, the inclination from the torque input shaft to the output gear is increased by changing the inclination angle of the rotating shaft of the power roller so that the peripheral surface of the power roller comes into contact with the vicinity of the outer periphery of the input disk and the vicinity of the center of the output disk, respectively. Conversely, the torque input shaft is changed by changing the inclination angle of the rotation shaft of the power roller so that the peripheral surface of the power roller comes into contact with the vicinity of the center of the input disk and the vicinity of the outer periphery of the output disk, respectively. From the output gear to the output gear. Further, an intermediate speed ratio between the two can be obtained almost steplessly by appropriately adjusting the inclination angle of the rotating shaft of the power roller.

[0004] Further, two sets of toroidal transmission mechanisms each comprising an input disk, a power roller, and an output disk are connected in parallel with a parallel connected double-cavity toroidal type with one output gear interposed therebetween. Step transmissions are being considered. In the case of a toroidal-type continuously variable transmission using this method, the rotational motion input to the torque input shaft follows the same operation principle as the above-described toroidal-type transmission mechanism, and the rotational motion in the opposite direction from the two input disks. The rotation torque of the torque input shaft is distributed to the two toroidal type transmission mechanisms because they are respectively transmitted to the two output disks which are attached to be back-to-back and are taken out from one output gear. Be paid.
Therefore, there is an advantage that a larger input torque can be accommodated with a margin.

In a double-cavity toroidal type continuously variable transmission, a large shaft load is applied to an output gear driven in both directions. Therefore, if the torque input shaft is supported only at both ends of the shaft, the torque input shaft is The torque input shaft is deformed by the bending force acting on the shaft. Also, when each output disk that transmits the driving force to the output gear is moved in a direction away from the input disk along the torque input shaft, the output disk maintains a frictional contact state for rotating by contacting with each power roller. No longer possible, causing idling of the power roller. Bearings are installed between each output disk and output gear, and the support wall connected to the outer ring of this bearing is fixed to the casing in order to prevent the drive power loss from increasing and the transmission efficiency from decreasing due to these effects. Thus, the support at the intermediate portion of the torque input shaft and the positioning of each output disk in the direction of the torque input shaft are performed.

FIG. 5 shows an example of a double-cavity toroidal type continuously variable transmission as described above. A first toroidal transmission mechanism composed of an input disk 11, a power roller 12, and an output disk 13 and a second toroidal transmission mechanism composed of an input disk 21, a power roller 22, and an output disk 23 The output disks 13 and 23 are mounted so that the output disks 13 and 23 are back-to-back.
An output gear 3 is disposed between the two. Further, between the first toroidal transmission mechanism and the second toroidal transmission mechanism, the output disk 1 extended along the torque input shaft 7 is provided.
The output gear shaft 4 and the output disk 23 which are part of
Are connected by fitting through an output gear 3.

[0007] In the example shown in the figure, between the output disc 13 and the output gear 3 of the first toroidal transmission, two gears are provided.
The pair of angular bearings 5 and 6 are arranged to be back-to-back. Each of these angular bearings 5 and 6 has an inner ring and an outer ring, and a plurality of balls held between the inner ring and the outer ring roll in the circumferential direction of the torque input shaft, so that each output is provided. The thrust and radial loads applied from the disks 13 and 23 to the output gear 3 are supported. The inner ring of the angular bearing 5 is mounted so as to be in contact with the end face of the output disk 13 and the side surface of the output disk 13 along the torque input axis. The inner ring of the angular bearing 6 is mounted on the end face of the output gear 3 and the torque input axis of the output disk 13. Is arranged to be in contact with the side surface along Also,
Each outer ring of the angular bearings 5 and 6 is connected to a support wall 8 fixed to the casing 7 with bolts or the like on the outer surfaces thereof.

FIG. 6 shows an example of a double-cavity toroidal type continuously variable transmission in which the output disk 13 and the output disk 23 are connected via an output gear shaft 4 integrally formed with the output gear 3. Is shown. The output gear 3 arranged between the output discs 13 and 23 is integrated with the output gear shaft 4,
Output disks 13 and 23 are respectively connected to both ends of. In this example, between the output disk 13 of the first toroidal type transmission mechanism and the output gear 3 and between the output gear 3 and the output disk 23 of the second toroidal type transmission mechanism, the angular bearings 5 and 6 are respectively provided on the back. The angular bearings 5 and 6 support the thrust and radial loads applied to the output gear 3 from the output disks 13 and 23 by these angular bearings 5 and 6. The inner races of the angular bearings 5 and 6 are in contact with the end faces of the output disks 13 and 23, respectively, and are connected to the end face of the output gear 3 and the side face of the output gear shaft 4, respectively. The outer races of the angular bearing 5 and the angular bearing 6 are connected to support walls 8 and 9 on the outer surfaces, respectively, and the support walls 8 and 9 are fixed to the casing 7 using bolts or the like.

[0009]

The support wall of the double-cavity toroidal type continuously variable transmission as described above has a complicated shape, so that it is not easy to machine the support wall and the number of components is large. As a result, not only does the total weight increase, but also unnecessary time and labor are required when performing processing work, assembling work, maintenance work, etc., and the processing cost and assembling of the entire toroidal-type continuously variable transmission are reduced. This causes an increase in cost and maintenance cost.

Further, in the above-described angular bearing of the double-cavity toroidal type continuously variable transmission, the outer ring is connected to the support wall by being fixedly fitted into a hole provided in the support wall, so that the bearing is fixed to the casing. The strength cannot be sufficiently secured. As a result, when a large thrust load is applied, creep occurs between the hole and the inner wall of the hole, and the degree of adhesion of the fitting surface is reduced.

SUMMARY OF THE INVENTION The present invention has been made in view of the above circumstances, and an object of the present invention is to increase the joint strength between a bearing and a casing and reduce the number of parts, thereby achieving a machining step, an assembly process, and maintenance. It is an object of the present invention to provide a bearing for a double-cavity toroidal-type continuously variable transmission that simplifies the process and reduces the weight of the entire transmission.

[0012]

SUMMARY OF THE INVENTION The present invention comprises two sets of toroidal speed change mechanisms having an input disk, an output disk, and a power roller abutted and held between these disks for transmitting a driving force between the two disks. The output disk and the output of a double-cavity toroidal continuously variable transmission in which two output disks of each of the toroidal transmission mechanisms are coupled back to back via an output gear shaft that rotates integrally with an output gear. The present invention relates to a bearing of a double-cavity toroidal type continuously variable transmission provided between a gear and supporting a load in a thrust direction and a radial direction acting on the output gear. Each outer ring is provided with a flange extending in a radial direction of the torque input shaft, and an outer edge of each flange is provided with a toroidal-type continuously variable transmission. It is achieved by fixing directly to the casing.

[0013]

FIG. 1 shows an embodiment of a bearing of a double-cavity toroidal type continuously variable transmission according to the present invention. Elements other than the bearing portion shown here can be configured in the same manner as a conventional double-cavity toroidal type continuously variable transmission. In this example,
By the output gear shaft 4 integrated with the output gear 3,
The output disk 13 of the first toroidal transmission and the second
The output disk 23 of the toroidal type transmission mechanism is connected, and the angular bearings 5 and 6 are disposed between the output disk 13 and the output gear 3 so as to be back-to-back. These angular bearings 5 and 6 are provided with an inner ring and an outer ring, respectively, similarly to a conventional bearing, and a plurality of balls that are sandwiched between the inner ring and the outer ring and roll over the circumferential direction of the torque input shaft. Accordingly, the load in the thrust direction and the radial direction applied from each of the output disks 13 and 23 to the output gear 3 is supported. The inner ring of the angular bearing 5 is attached so as to be in contact with the end surface of the output disk 13 and the side surface of the output disk 13 along the torque input shaft.
Of the output gear 3 and the side surface of the output disk 13 along the torque input axis.
In this example, the two inner rings of the angular bearing 5 and the angular bearing 6 have an integral structure connected along the torque input shaft. However, as in the conventional case, the inner rings of each angular bearing are separated from each other. You may. On the other hand, angular bearing 5,
Each of the outer rings 6 has an integral structure joined in the lateral direction of the torque input shaft similarly to the inner ring, and a flange 51 extending in a radial direction of the torque input shaft is integrally provided on an outer surface thereof. In the bearing of the present invention, the outer edges of the flange 51 are directly fixed to the casing 7 using bolts or the like, thereby realizing the connection between the angular bearings 5 and 6 and the casing 7.

FIG. 2 shows another embodiment of the bearing of the double-cavity toroidal type continuously variable transmission according to the present invention, which is connected to both ends of an output gear shaft 4 integrated with an output gear 3. The angular bearings 5 and 6 are back-to-back between the output disk 13 and the output gear 3 of the first toroidal transmission mechanism and between the output gear 3 and the output disk 23 of the second toroidal transmission mechanism, respectively. It is arranged to be. The angular bearings 5 and 6 support loads in the thrust direction and the radial direction applied from the output disks 13 and 23 to the output gear 3. The inner rings of the angular bearings 5 and 6 are in contact with the end faces of the output disks 13 and 23, respectively, and are connected to the end face of the output gear 3 and the side face of the output gear shaft 4, respectively. Further, flanges 51, 61 extending radially of the torque input shaft integrally formed with the respective outer rings are provided on the outer surfaces of the respective outer rings of the angular bearings 5, 6, and the outer edges of the flanges 51, 61 are bolted. The angular members 5, 6 and the casing 7 are connected to each other by directly fixing them to the casing 7, for example.

With the above-described configurations, in the bearing of the double-cavity toroidal type continuously variable transmission according to the present invention, there is no fitting portion between the bearing outer ring and the casing, and the casing is securely fixed to the casing. Does not occur. Further, since the number of components is smaller than that of the conventional structure, the design can be made lighter, and the steps of machining, assembling and maintenance can be reduced, so that the cost can be reduced. further,
In the toroidal type continuously variable transmission incorporating the bearing of the present invention, the dimension in the direction of the torque input shaft is shorter than before.

FIGS. 3 and 4 show modifications of the embodiment of FIGS. 1 and 2, respectively, in which the functions of the inner rings of the angular bearings 5, 6 are formed on the side surfaces of the output gear shaft 4 by projections. The bearing race formed on the member is replaced. With this configuration, the number of components can be further reduced, and the fixing strength of the torque input shaft can be further increased.

In each of the embodiments shown in FIGS. 1 to 4, the angular bearings 5 and 6 are arranged so as to be back-to-back, but these angular bearings 5 and 6 are arranged so as to be face-to-face. Also in this case, the same effect can be obtained by providing a flange extending in the radial direction of the torque input shaft on the outer surface of the outer ring and directly fixing the outer edge of the flange to the casing 7. In the above, an example was described in which the bearing disposed between two output disks and one output gear was an angular bearing. However, the bearing of the present invention supports loads in the thrust direction and the radial direction. The bearing is not necessarily limited to an angular bearing, and may be, for example, a tapered roller bearing, a deep groove ball bearing, a three-point contact ball bearing, or a four-point contact ball bearing.

[0018]

As described above, according to the bearing of the double-cavity toroidal type continuously variable transmission according to the present invention, the coupling strength between the bearing and the casing can be kept high, so that the driving force loss is reduced. In addition, the reduction in the number of components makes it possible to simplify the machining process, the assembling process, and the maintenance process, reduce the weight of the entire transmission, and reduce the dimension in the torque input axis direction.

[Brief description of the drawings]

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

FIG. 2 is an axial sectional view showing another embodiment of the bearing of the double-cavity toroidal type continuously variable transmission according to the present invention.

FIG. 3 is an axial sectional view showing a modified example of the bearing of the double-cavity toroidal type continuously variable transmission according to the present invention shown in FIG. 1;

FIG. 4 is an axial sectional view showing an example in which the bearing of the double-cavity toroidal type continuously variable transmission shown in FIG. 2 is modified.

FIG. 5 is an axial sectional view showing an example of a conventional double-cavity toroidal-type continuously variable transmission including a bearing.

FIG. 6 is an axial sectional view showing another example of a conventional double-cavity toroidal type continuously variable transmission including a bearing.

[Explanation of symbols]

 Reference Signs List 3 output gear 4 output gear shaft 5, 6 angular bearing 7 casing 8, 9 support wall 11, 21 input disk 12, 22 power roller 13, 23 output disk 51, 61 flange

Claims (1)

[Claims] 1. A toroidal transmission mechanism comprising two sets of an input disk and an output disk and a power roller abutted and held between these disks and transmitting a driving force between the two disks. Two output disks are provided between the output disk and the output gear of the double-cavity toroidal-type continuously variable transmission that is coupled back to back via an output gear shaft that rotates integrally with the output gear; In a bearing of a double-cavity toroidal type continuously variable transmission that supports a load in a thrust direction and a radial direction acting on the output gear, each outer ring of the bearing has a flange extending in a radial direction of a torque input shaft. An outer edge of each of the flanges is directly fixed to a casing of the toroidal type continuously variable transmission. Bearing for cavity type toroidal type continuously variable transmission.