JP3629898B2 - Toroidal continuously variable transmission - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a toroidal-type continuously variable transmission used as a transmission for an automobile, for example.
[0002]
[Prior art]
A toroidal-type continuously variable transmission, which has been studied mainly as a transmission for automobiles, is sandwiched between an input disk and an output disk, each of which has an arcuate concave cross section on the surfaces facing each other. A toroidal transmission mechanism having a structure combined with a rotatable power roller. At this time, the input disc, is attach to the rotation available-integrally with the torque input shaft, while the output disk, moves in a direction away from the relatively rotatable and the input disc against the torque input shaft Is mounted opposite to the input disk so that is limited.
[0003]
In the toroidal transmission mechanism as described above, when the input disk rotates, the output disk rotates in reverse via the power roller. Therefore, the rotational motion input to the torque input shaft is converted to the output disk as a reverse rotational motion. Transmitted and taken out. At this time, the speed of rotation 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 is in contact with the vicinity of the outer periphery of the input disk and the center of the output disk. On the contrary, the torque input shaft is changed by changing the tilt angle of the rotation shaft of the power roller so that the peripheral surface of the power roller is in contact with the vicinity of the center of the input disk and the vicinity of the outer periphery of the output disk. To the output gear. Further, an intermediate gear ratio can be obtained almost steplessly by appropriately adjusting the inclination angle of the rotating shaft of the power roller.
[0004]
Furthermore, a double-cavity toroidal continuously variable transmission having a structure in which two sets of such toroidal transmission mechanisms are prepared and each output disk is combined so as to sandwich the output gear is considered. FIG. 8 is a side sectional view showing an example of such a double cavity toroidal continuously variable transmission. A first toroidal transmission mechanism 1 including an input disk 11, a power roller 12, and an output disk 13, and a second toroidal transmission mechanism 2 including an input disk 21, a power roller 22, and an output disk 23. Are attached so that the output disks 13 and 23 face each other, and the output gear 3 is disposed between the output disks 13 and 23. The first toroidal transmission mechanism 1 and the second toroidal transmission mechanism 2 are coupled via an output gear shaft 4 formed integrally with the output gear 3.
[0005]
Also in the toroidal transmission mechanism of the double cavity type exemplified here, according to the same operating principle as the above-described toroidal transmission mechanism, the output disk 13 is configured such that the rotational motion input to the torque input shaft 7 is the reverse rotational motion. 23 and can be taken out from the output gear 3. In particular, in the case of a double cavity type toroidal type transmission mechanism, the rotational torque of the torque input shaft 7 is distributed and borne by the two toroidal type transmission mechanisms 1 and 2, so that a larger torque can be handled with a margin. There is an advantage that can be.
[0006]
Angular bearings 5 and 6 are provided between the output disk 13 and the output gear 3 of the first toroidal transmission mechanism 1 and between the output gear 3 and the output disk 23 of the second toroidal transmission mechanism 2, respectively. It is arrange | positioned and the reaction force at the time of the output gear 3 rotating is supported by these angular bearings 5 and 6. In the angular bearings 5 and 6, the inner rings 51 and 61 are in contact with the end surfaces of the output disks 13 and 23 via the plates 50 and 60, and are in contact with the side surfaces of the output gear shaft 4 and the end surface of the output gear 3. The outer rings 52 and 62 are in contact with the output gear casing 8, and the rolling elements 54 and 64 are held by the retainers 53 and 63 held between the outer rings 52 and 62 and the inner rings 51 and 61. Thus, the rotational difference between the outer rings 52 and 62 and the inner rings 51 and 61 is absorbed.
[0007]
In a toroidal transmission mechanism that rotates at high speed during operation, lubricating oil is supplied from a lubricating pump (not shown) in order to prevent seizure of the rotating portion. Lubricating oil pressure-fed through the hollow torque input shaft 7 to the toroidal-type continuously variable transmission portion is moved out of the torque input shaft 7 through an oil supply hole 71 provided in the side wall of the torque input shaft 7. After being sent out and lubricating the rotating parts such as the output disks 13 and 23 and the output gear 4, they are recovered and reused.
[0008]
The lubricating oil delivered from the oil supply hole 71 on the side wall of the torque input shaft 7 passes through the oil supply hole 41 penetrating the side wall of the output gear shaft 4 and then provided to the inner rings 51 and 61 of the angular bearings 5 and 6. The oil is supplied to the vicinity of the rolling elements 54 and 64 through the oil supply grooves 55 and 65. FIG. 9 is an enlarged view of the vicinity of an angular bearing mounting portion of such a conventional double cavity type toroidal continuously variable transmission. The oil supply grooves 55 and 65 are formed on the contact surface with the output gear shaft side surface of the inner ring of each angular bearing and on the contact surface with the output gear end surface.
[0009]
[Problems to be solved by the invention]
Since each part of the toroidal-type continuously variable transmission rotates at a high speed, a strong centrifugal force acts on the lubricating oil delivered through the oil supply hole on the side wall of the torque input shaft. On the other hand, in the angular bearing having the oil supply groove as described above, the outlet of the oil supply groove is positioned closer to the output gear than the rolling element of the angular bearing because of its structure. For this reason, most of the lubricating oil that has passed through the oil supply groove of the inner ring of the angular bearing is diffused in the radial direction along the end face of the output gear in a short time, so that the rolling elements of the angular bearing are sufficiently lubricated. Absent. If the angular bearing is not sufficiently lubricated and receives a large load and is rotated at a high speed, the angular bearing causes early separation, which leads to a decrease in the reliability of the entire toroidal continuously variable transmission. The oil supply groove is formed continuously along the contact surface between the inner ring of each angular bearing and the side surface of the output gear shaft, and the contact surface between the inner ring of each angular bearing and the output gear end surface. As the amount of processing increases, the processing steps become complicated, and the labor and cost required for manufacturing increase.
[0010]
Further, the plate between the output disk and the inner ring of the angular bearing is deformed by receiving an excessive load from the output disk, and the output disk itself is also deformed, so that fretting wear occurs between them. Further, when a plate is not disposed between the output disk and the angular bearing inner ring, since the lubrication between the output disk and the angular bearing inner ring is not sufficiently performed, fretting wear also occurs. When wear powder generated by such fretting wear enters around the rolling elements of an angular bearing, it not only causes abnormal noise and rotational resistance, but also may cause damage to the angular bearing. This is a problem when the step transmission operates.
[0011]
The present invention has been made under the circumstances as described above, and an object of the present invention is toroidal that can reliably lubricate the periphery of the rolling element of the angular bearing and suppress fretting wear between the output disk and the angular bearing. The object is to provide a type continuously variable transmission.
[0012]
[Means for Solving the Problems]
The present invention includes an input disk which is attach to the rotation available-integrally with the torque input shaft, to move in the direction away from the relatively rotatable and said input disc with respect to the torque input shaft is limited The output disk mounted opposite to the input disk, and the rotation of the input disk having an arcuate concave cross section and the rotation of the output disk held between the disks so as to contact each other. 2 sets of toroidal type speed change mechanisms comprising a flexible power roller are provided through an output gear shaft formed integrally with an output gear and mounted so as to be rotatable relative to the torque input shaft. The output disks of the two sets of toroidal transmissions are coupled to each other, and the output disks of the two sets of toroidal transmissions and the Inner rings of two angular bearings arranged between the force gears are in contact with the output disk end face, the output gear shaft side face, and the output gear end face, respectively, and the outer rings of the two angular bearings are connected to the output gear casing. The present invention relates to a toroidal-type continuously variable transmission that is in contact with each other, and an object of the present invention is to provide an oil supply groove along a radial direction of an output disk side end surface of each inner ring of the two angular bearings or two output disks. Lubricating oil formed on the output gear side end face and supplied through the hollow torque input shaft to lubricate each rotating part, respectively, on the wall surface of the torque input shaft and the wall surface of the output gear shaft. After passing through the oil supply hole penetrating, the oil is delivered to the periphery of the rolling elements of the two angular bearings through the oil supply groove. It is achieved by. Alternatively, oil supply grooves along the radial direction may be formed on the output gear side end surfaces of the output disks of the two toroidal transmission mechanisms, respectively. Alternatively, oil supply grooves along the radial direction may be formed on the output disk side end surfaces of the inner rings of the two angular bearings.
[0013]
DETAILED DESCRIPTION OF THE INVENTION
FIG. 1 is a side sectional view showing one embodiment of the toroidal type continuously variable transmission according to the present invention in contrast to the conventional example of FIG. 8, and is used in FIG. 8 for components having the same function. The same reference numerals are given. The toroidal type continuously variable transmission of the present invention is characterized by the shape of the oil supply groove provided in the angular bearing of the double cavity type toroidal type continuously variable transmission. The configuration can be the same as that of the cavity-type toroidal-type continuously variable transmission.
[0014]
A first toroidal transmission mechanism 1 including an input disk 11, a power roller 12, and an output disk 13, and a second toroidal transmission mechanism 2 including an input disk 21, a power roller 22, and an output disk 23. Are attached so that the output disks 13 and 23 face each other, and the output gear 3 is disposed between the output disks 13 and 23. The first toroidal transmission mechanism 1 and the second toroidal transmission mechanism 2 are coupled via an output gear shaft 4 formed integrally with the output gear 3.
[0015]
Further, between the output disk 13 and the output gear 3 of the first toroidal transmission mechanism 1 and between the output gear 3 and the output disk 23 of the second toroidal transmission mechanism 2, there are angular bearings 5 and 6, respectively. It is arrange | positioned and the reaction force at the time of the output gear 3 rotating is supported by these angular bearings 5 and 6. In angular bearing 5 and 6, the inner ring 51 and 61 is in contact with the end surface of the side and the output gear 3 of the output gear shaft 4 to the end surface of the output disk 13 and 23, the outer ring 52 and 62, the output gear casing 8 Is in contact with A plurality of rolling elements 54 and 64 held by the cages 53 and 63 are sandwiched between the outer rings 52 and 62 and the inner rings 51 and 61, and the outer rings are rolled by the rolling elements 54 and 64. The rotational difference between 52 and 62 and the inner rings 51 and 61 is absorbed.
[0016]
2 is an enlarged view of the vicinity of the angular bearing mounting portion of the embodiment of the double cavity type toroidal continuously variable transmission of the present invention shown in FIG. 1, and has the same functions as the components of the conventional example shown in FIG. The same reference numerals are given to the portions having. FIG. 3 is a front view of the angular bearings 5 and 6 as viewed from the output disks 13 and 23 side of the toroidal transmission mechanisms 1 and 2. In the double cavity type toroidal continuously variable transmission according to the present invention, the oil supply grooves 55a and 65a along the radial direction are formed on the contact surfaces of the inner rings 51 and 61 of the angular bearings 5 and 6 with the output disks 13 and 23, respectively. Is formed. In the present embodiment, three oil supply grooves 55a and 65a are provided along the circumferences of the inner rings 51 and 61, respectively, but the number of oil supply grooves 55a and 65a is not limited. Similarly to the conventional example, after the lubricating oil sent from the oil supply hole 71 provided on the side wall of the torque input shaft 7 passes through the oil supply hole 41 penetrating the side wall of the output gear shaft 4, It is supplied to the vicinity of the rolling elements 54 and 64 through oil supply grooves 55a and 65a provided in the inner rings 51 and 61 of the angular bearings 5 and 6, respectively.
[0017]
The outlets of the oil supply grooves 55a, 65a provided in such a place are closer to the output disks 13, 23 than the rolling elements 54, 64 of the angular bearings 5, 6. Therefore, even if a strong centrifugal force is acting on the lubricating oil due to the high-speed rotation of the toroidal continuously variable transmission, the lubricating oil that has passed through the oil supply grooves 55a and 65a is in the vicinity of the rolling elements 54 and 64 of the angular bearings 5 and 6. Surely sent out. Furthermore, since a sufficient amount of lubricating oil is supplied between the output disks 13 and 23 and the inner rings 51 and 61 of the angular bearings 5 and 6, the output disks 13 and 23 and the inner rings 51 and 61 of the angular bearings 5 and 6 There is no need to place a plate between them, and no fretting wear occurs.
[0018]
FIG. 4 is an enlarged view of the vicinity of the angular bearing mounting portion of another embodiment of the double cavity type toroidal continuously variable transmission according to the present invention. In this embodiment, the oil supply grooves 55a and 65a formed on the contact surfaces of the inner rings 51 and 61 of the angular bearings 5 and 6 with the output disks 13 and 23 are tapered to increase the opening area on the outlet side. It has a cross section of shape. By doing in this way, it becomes easier for lubricating oil to spread around the rolling elements 54 and 64.
[0019]
FIG. 5 is a side sectional view showing still another embodiment of the double cavity type toroidal continuously variable transmission according to the present invention in comparison with the conventional example of FIG. 8, and FIG. 6 is shown in FIG. FIG. 5 is an enlarged view of the vicinity of an angular bearing mounting portion in an embodiment of the double cavity type toroidal continuously variable transmission. In this embodiment, instead of providing the oil supply grooves 55a and 65a in the inner rings 51 and 61 of the angular bearings 5 and 6, the inner rings of the angular bearings 5 and 6 of the output disks 13 and 23 of the toroidal transmission mechanisms 1 and 2, respectively. Oil supply grooves 131 and 231 are formed on the contact surfaces with 51 and 61. FIG. 7 is a front view of the output disk of the toroidal transmission mechanism in this embodiment as viewed from the output gear side. Even when the oil supply grooves 131 and 231 are provided on the output disks 13 and 23 as in the present embodiment, the oil supply grooves 131 and 231 of the angular bearings 5 and 6 are provided in the same manner as when the oil supply grooves 131 and 231 are provided. Since the outlet is located closer to the toroidal transmission mechanisms 1 and 2 than the rolling elements 54 and 64 of the angular bearings 5 and 6, the lubricating oil is reliably delivered to the vicinity of the rolling elements 54 and 64 of the angular bearings 5 and 6. In this embodiment, three oil supply grooves 131 and 231 are provided over the circumference of the output disks 13 and 23, respectively, but the number of oil supply grooves 131 and 231 is not limited.
[0020]
【The invention's effect】
As described above, according to the toroidal type continuously variable transmission of the present invention, lubrication around the rolling elements of the angular bearing can be reliably performed, and fretting wear between the output disk and the angular bearing can be suppressed. Also, since the oil supply groove is formed only on one surface of the inner ring of each angular bearing or on the output disk, the amount of parts processed can be reduced, the processing process is simplified, and the labor and cost required for manufacturing are reduced. Reduction can be expected.
[Brief description of the drawings]
FIG. 1 is a side sectional view showing an embodiment of a toroidal continuously variable transmission according to the present invention.
FIG. 2 is an enlarged view of the vicinity of an angular bearing mounting portion in the embodiment of the toroidal type continuously variable transmission of the present invention shown in FIG. 1;
FIG. 3 is a front view of the angular bearing of the embodiment shown in FIG. 2 as viewed from the output disk side of the toroidal type transmission mechanism.
FIG. 4 is an enlarged view of the vicinity of an angular bearing mounting portion in another embodiment of the toroidal continuously variable transmission of the present invention.
FIG. 5 is a side sectional view showing still another embodiment of the toroidal continuously variable transmission according to the present invention.
6 is an enlarged view of the vicinity of an angular bearing mounting portion in the embodiment of the toroidal type continuously variable transmission shown in FIG. 5. FIG.
7 is a front view of the output disk of the toroidal transmission mechanism of the embodiment shown in FIG. 6 as viewed from the output gear side.
FIG. 8 is a side sectional view showing an example of a conventional toroidal-type continuously variable transmission.
9 is an enlarged view of the vicinity of an angular bearing mounting portion in the example of the conventional toroidal-type continuously variable transmission shown in FIG.
[Explanation of symbols]
1, 2 Toroidal transmission mechanism 3 Output gear 4 Output gear shaft 5, 6 Angular bearing 7 Torque input shaft 8 Output gear casing 11, 21 Input disk 12, 22 Power roller 13, 23 Output disk 41, 71 Oil supply hole 50, 60 Plate 51, 61 Inner ring 52, 62 Outer ring 53, 63 Cage 54, 64 Rolling element 55, 55a, 65, 65a, 131, 231 Oil supply groove

Claims (3)

It said to be limited to move in the direction away an input disk which is attach to the rotation available-integrally, from a relatively rotatable and said input disc with respect to the torque input shaft with respect to torque input shaft An output disk that is mounted to face the input disk, and a rotatable power roller that is sandwiched between the input disk and the output disk, each having an arcuate concave section, so as to abut against the mutually facing surfaces of the output disk The two toroidal transmission mechanisms are formed via an output gear shaft that is integrally formed with an output gear and is rotatably attached to the torque input shaft. Output disks of the transmission mechanism are coupled to each other, and the output disks of the two sets of toroidal transmission mechanisms and the output gear The inner ring of the two angular bearings arranged on the toroidal is in contact with the output disk end face, the output gear shaft side face, and the output gear end face, respectively, and the outer ring of the two angular bearings is in contact with the output gear casing. In the type continuously variable transmission, oil supply grooves along the radial direction are respectively formed on the output disk side end surfaces of the inner rings of the two angular bearings or on the output gear side end surfaces of the two output disks , After the lubricating oil supplied through the hollow torque input shaft to lubricate the rotating part passes through the oil supply holes penetrating the wall surface of the torque input shaft and the wall surface of the output gear shaft, the oil supply groove A toroidal-type continuously variable transmission characterized by being sent to the periphery of the rolling elements of the two angular bearings. The toroidal continuously variable transmission according to claim 1, wherein oil supply grooves along the radial direction are formed on the output gear side end surfaces of the output disks of the two toroidal transmission mechanisms, respectively. 2. The toroidal continuously variable transmission according to claim 1, wherein an oil supply groove along the radial direction is formed on an output disk side end surface of each inner ring of the two angular bearings.

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