JPH0557494U - Toroidal type continuously variable transmission - Google Patents

Abstract

(57) [Summary] (Correction) [Purpose] To provide a toroidal-type continuously variable transmission that can improve transmission efficiency and shorten axial length. [Structure] A shaft member bearing 19 is provided between a tubular member 4 and a shaft member 15, and a tubular member bearing 5 is provided between a housing 1 and the tubular member 4, so that both bearings are axially aligned. It is not necessary to install them side by side, and the axial length is shortened. Further, since the oil supply passage rotates integrally with the tubular member 4,
The lubricating oil supplied from the oil supply passage is the shaft member bearing 19
It doesn't resist when it rotates.

Description

[Detailed description of the device]

[0001]

[Industrial application]

 The present invention relates to a toroidal type continuously variable transmission used in a vehicle or the like.

[0002]

[Prior Art]

 A toroidal continuously variable transmission is known as a transmission capable of continuously changing the speed ratio. Such a toroidal type continuously variable transmission is described in, for example, Japanese Utility Model Laid-Open No. 62-158249. FIG. 3 is an axial sectional view of a toroidal type continuously variable transmission described in JP-A-62-158249. The configuration and operation of a toroidal type continuously variable transmission according to the prior art will be described below with reference to FIG. An input shaft 102 extends in the housing 101. An input shaft 102, whose right end is connected to a rotating portion of an engine (not shown), is rotatably supported by a bearing 103 and 104 with respect to the housing 101. A disc portion 105 is coaxially and immovably attached to the input shaft 102 near the bearing 104 so that the input shaft 102 and the disc portion 105 rotate integrally. The input discs 107 are arranged side by side on the disc portion 105, and a loading cam 106 is provided between the input disc 107 and the disc portion 105. The loading cam 106 presses the input disc 107 against the disc portion 105 with an appropriate force, and between the loading cam 106 and the disc portion 105 and between the loading cam 106 and the input disc 107. A predetermined frictional force is generated in each of the discs, and thus the frictional force causes the input disc 107 to rotate integrally with the disc portion 105.

An output disc 109 is provided so as to face the input disc 107, and a power roller 108 is interposed between the input disc 107 and the output disc 109 with oil interposed therebetween to be rotatable and rotatable. Is provided. The output disk 109 has an integrally formed gear 110, and is rotatably supported by a bearing 111 with respect to the housing 101. The gear 111 meshes with an output gear (not shown), and the output gear is connected to an axle (not shown). The power roller 108 is also rotatable about an axis perpendicular to the paper surface by a support mechanism (not shown) so that the contact position with respect to both disks can be changed. The housing 101 near the left end of the input shaft 102 is provided with a supply passage 112 connected to a lubricating oil supply device (not shown). Further, an oil passage 113 extending in the axial direction is provided at the left end of the input shaft 102 corresponding to the supply passage 112, and the oil supply passage 114 connects the inner end of the oil passage 113 and the outer periphery of the input shaft 102. Is provided. The oil supply passage 114 faces a space defined between the bearing 103 and the bearing 111.

Next, the operation of the toroidal type continuously variable transmission shown in FIG. 3 will be described below. The rotational force of the rotating portion of the engine (not shown) is transmitted to the disc portion 105 via the shaft member 2. The rotational force transmitted to the disc portion 105 is transmitted to the input disk 107 via the loading cam 106.

Oil is present between the input disk 107 and the power roller 108. Therefore, the shearing force of the oil acts between the input disk 107 and the power roller 108 as the input disk 107 rotates. To do. Due to the action of this shearing force, the power roller 108 rotates with almost no slippage with respect to the input disc 107, and the rotational force transmitted to the input disc is transmitted to the power roller 109. Similarly, the rotational force is transmitted from the power roller 108 to the output disc 109, and further the rotational force is transmitted from the output disc 109 to the axle (not shown) via the gear 110. When the power roller 108 rotates about an axis perpendicular to the paper surface, the rotational speed of the output disk 109 with respect to the rotational speed of the input disk 107 changes according to the contact position. As a result, continuously variable transmission is achieved.

[0006]

[Problems to be solved]

 By the way, the bearing 103 that supports the input shaft 102 and the bearing 111 that supports the output disk 109 are lubricated by the lubricating oil supplied from the oil supply passage 114. The rotation speeds of the input shaft 102 and the output disk 114 are the rotation speeds of the inner ring of the bearing 103 and the inner ring of the bearing 111, respectively. In this case, since the oil supply passage 114 is provided on the input shaft 102, the lubricating oil is tangentially discharged from the oil supply passage 114 at the speed of the input shaft 102, that is, the inner ring of the bearing 103. Therefore, this lubricating oil does not create resistance when the bearing 103 rotates. However, unless the speed ratio of the output disk 109 is 1: 1, the output disk 109 has a rotation speed different from that of the input shaft 102. Therefore, the lubricating oil discharged from the oil discharge passage 114 has a speed difference when the bearing 111 rotates. A corresponding resistance (stirring resistance) is generated. Such resistance has been one of the causes for reducing the transmission efficiency of the transmission. Further, the bearing 103 and the bearing 111 are arranged side by side in the axial direction, and are configured to be long in the axial direction. Such a configuration has been a problem in the installation design of the continuously variable transmission. An object of the present invention is to provide a toroidal type continuously variable transmission that can improve transmission efficiency and can shorten axial length.

[0007]

[Means for solving the problem]

 The toroidal type continuously variable transmission according to the present invention comprises a housing, an input disc, an output disc, and one of the input disc and the output disc which are brought into contact with the input disc and the output disc to roll. A roller means for transmitting power to the other side, a shaft member for transmitting power by being connected to any one of the input side disc and the output side disc, and the shaft member provided so as to include the shaft member. A tubular member that is connected to the other of the side disc and the output side disc to transmit power, and is provided between the tubular member and the shaft member, and the shaft member is rotatable with respect to the tubular member. And a tubular member bearing that is provided between the housing and the tubular member and that rotatably supports the tubular member with respect to the housing, and lubricates the shaft member bearing. And a pumping means for pumping the lubricating oil, and a pumping part for pumping the lubricating oil and an oil supply passage connected to the pumping part for supplying the pumped lubricating oil to the bearing. And the oil supply passage rotates integrally with the tubular member.

[0008]

[Action]

 Since the shaft member bearing is provided between the tubular member and the shaft member, and the tubular member bearing is provided between the housing and the tubular member, both bearings need to be arranged side by side in the axial direction. And the axial length is shortened. Further, since the oil supply passage rotates integrally with the tubular member, the lubricating oil supplied from the oil supply passage does not resist the rotation of the shaft member bearing.

[0009]

【Example】

 An embodiment of the present invention will be described below with reference to the drawings. FIG. 1 is a partial sectional view of a toroidal type continuously variable transmission according to the present invention. In FIG. 1, the left side of the housing 1 is the input side, and the right side is the output side. The housing 1 includes a left half portion 1a and a right half portion 1b. From the input side, the configuration of the toroidal type continuously variable transmission according to the present invention will be described. The disc portion 2 having the spline portion 2a at the center is connected to a power source (not shown) by the spline portion 2a. The disk portion 2 is provided with several bolt holes 2b at equal intervals in the vicinity of the outer circumference. A tubular member 4 is provided adjacent to and coaxial with the disc portion 2. The tubular member 4 has a configuration in which a flange portion 4a, a large circular pipe portion 4b, and a small circular pipe portion 4c are connected in series in the axial direction. The flange portion 4a is provided with several female screw portions at positions corresponding to the bolt holes 2b of the disc portion 2, and the disc portion 2 and the tubular member 4 are fastened by the bolts 3.

The outer circumference of the large circular tube portion 4b of the tubular member 4 is connected to the housing 1 by a tubular member bearing 5, and the outer circumference of the small circular tube portion 4c of the tubular member 4 is connected to the housing 1 by a bearing 6. More rotatably supported. A serration 4d is formed on the inner circumference of the small circular tube portion 4c. Adjacent to the small circular pipe portion 4c, there is provided a pressing member 9 configured to be coaxially connected to the circular plate 9a and the circular pipe 9b. A serration portion 9c is provided on the outer circumference of the circular pipe 9c, and the tubular member 4 is movable in the axial direction but is capable of transmitting the rotational force by engaging the serration 4d with the serration portion 9c of the pressing member 9. It is connected to the pressing member 9. A spacer 7 and a disc spring 8 are provided between the pressing member 9 and the free end of the small circular tube portion 4c of the tubular member 4, and the disc spring 8 connects the pressing member 9 and the tubular member 4 in the axial direction. They are urged in directions away from each other.

The pressing member 9 is adjacent to the input disk 12 with the loading roller 11 supported by the retainer 10 interposed therebetween. The input disk 12 has a substantially conical shape, the outer slope thereof has a toroidal shape, and has an opening 12a penetrating itself in the axial direction. The loading roller 11 comes into contact with both the pressing member 9 and the input disk 12, and the relative rotation of the pressing member 9 and the input disk 12 causes the input disk 12 to press the power roller assembly 13. There is.

An output disk 14 having the same outer slope is provided facing the input disk 12. Two power roller assemblies 13 are provided between the input disk 12 and the output disk 14. The power roller assembly 13 comprises a trunnion 13a, a shaft 13b, a bearing 13c and a roller portion 13d. The trunnion 13a is supported by the housing 1 by a structural member (not shown), and also supports the shaft 13b. The roller portion 13d is supported by the trunnion 13a via a bearing 13c, and is rotatable around a shaft 13b. The roller portion 13d is in contact with the input disk 12 and the output disk 14 via oil during use. The structural member supporting the trunnion 13a rotates the power roller assembly 13 about an axis perpendicular to the plane of the drawing. At this time, one power roller assembly rotates clockwise and the other rotates counterclockwise by the same amount. With the rotation of the power roller assembly 13, the effective diameters of the contact portion between the roller portion 13d and the input disk 12 and the contact portion between the roller portion 13d and the output disk 14 are reduced if one decreases. Changes to increase.

The output disk 14 has an opening 14 a that extends in the axial direction and penetrates the output disk 14, and a serration portion 14 b is formed on the inner periphery of the opening 14 a. A shaft member 15 extends through the opening 14a of the output disk 14, the opening 12a of the input disk, and the circular tube 9b of the pressing member 9. The output disk 14 is usually attached to the shaft member 15 by press fitting or the like, but may be serrated if necessary. The input disk 12 is supported by the shaft member 15 via a bearing 16, and the pressing member 9 is supported by the shaft member 15 via a bearing 17. Therefore, the input disk 11 and the pressing member 9 rotate independently of the shaft member 15. A male screw portion 15a is engraved on the left end of the shaft member 15, and a preload nut 18 is screwed into the male portion 15a. The outer circumference of the preload nut 18 is supported by the inner circumference of the great circular pipe portion 4b of the tubular member 4 via a shaft member bearing 19. Further, a spline portion 15b is formed at the right end of the shaft member 15, and the shaft member 15 is connected to a power absorption device (not shown) via the spline portion 15b.

Next, the bearing lubrication system in the toroidal type continuously variable transmission according to the present invention will be described. FIG. 2 is an enlarged view of the left side portion of the embodiment shown in FIG. In FIG. 2, a serration portion 4d is provided adjacent to the bearing 6 on the outer circumference of the small circular pipe portion 4c of the tubular member 4. The trochoid pump rotating part 20 is provided in a cavity 1c having an elliptical cross section when viewed from the axial direction, which is formed at the end of the right half part 1b of the housing 1 radially outward of the small circular pipe part 4c. There is. The rotating portion 20 has a disc shape, and the serration portion 20a provided on the inner circumference is engaged with the serration portion 4d of the tubular member 4. Therefore, the rotating part 20 rotates together with the tubular member 4. The left half 1a of the housing 1 and the cavity 1c form a pump inner space.

A lubricating oil supply passage (not shown) is provided in the right half portion 1b of the housing 1, and a lubricating oil discharge passage 1d is provided in the left half portion 1a. The lubricating oil discharge passage 1d communicates with a drain oil passage 4e that passes through the small circular pipe portion 4c in the radial direction. Although not shown in the figure, several drain oil passages 4e are provided at equal intervals, and the lubricating oil drain passage 1d has an inner end in the radial direction in an annular shape extending in the outer circumferential direction of the small circular pipe portion 4c. It communicates with the groove 4g. Therefore, the lubricating oil passage 1d always communicates with the drain oil passage 4e at any position. The oil drain passage 4e communicates with a space A defined between the tubular member 4 and the shaft member 15.

A space B defined by the shaft member bearing 19, the tubular member 4 and the disc portion 2 is provided outside the space A with the shaft member bearing 19 being separated therefrom. A circular tubular lid member 21 having one end closed is provided adjacent to the disc portion 2, and the lid member 21 cooperates with an O-ring 22 provided on the outer periphery thereof to prevent leakage of lubricating oil. It is supposed to do. The space B communicates with the space C through an axial oil discharge passage 4f that penetrates the great circular pipe portion 4b of the tubular member 4 in the axial direction. The space C is defined by the left half 1 a of the housing 1, the tubular member 4, and the tubular member bearing 5. The space C further communicates with an external tank (not shown) via the external discharge passage 23. A seal 24 is provided adjacent to the tubular member bearing 5 to prevent leakage of oil that lubricates the tubular member bearing 5.

Next, the operation of the toroidal type continuously variable transmission according to the present invention will be described below. In FIG. 1, the rotational force is transmitted to the tubular member 4 from the rotating portion of the engine (not shown) via the spline portion 2a. When the tubular member 4 rotates, the pressing member 9 rotates integrally therewith, and the input disk 12 is rotated via the loading roller 11. The rotation of the input disk 12 causes the output disk 14 to rotate via the roller portion 13d of the power roller assembly 13. In this case, the effective diameters of the contact portions of the input disc 11 and the output disc 14 in the roller portion 13d of the power roller assembly 13 shown in FIG. 1 are almost the same, so that the gear ratio is 1: 1. Is becoming From this state, when the upper power roller assembly 13 in FIG. 1 rotates counterclockwise and the lower power roller assembly 13 rotates clockwise, the power roller assembly 13 and the input disk 12 are separated from each other. Since the effective diameter of the contact portion of the power roller assembly 13 and the output disk 14 increases at the same time, the effective diameter of the contact portion of the power roller assembly 13 and the output disk 14 simultaneously increases, so that the gear ratio continuously changes toward the deceleration side. .. Obviously, when the power roller assemblies 13 rotate in the opposite directions, the gear ratio continuously changes to the increasing side. When the output disk 14 rotates, the shaft member 15 is rotated, and the rotational force is transmitted to the power absorbing device (not shown) via the spline portion 15b.

In FIG. 2, when the tubular member 4 rotates, the trochoid pump rotating part 20 rotates, and thereby the lubricating oil is pumped from the lubricating oil supply passage (not shown) to the lubricating oil discharge passage 1d. The lubricating oil pumped is discharged into the space A via the oil discharge passage 4e (which serves as an oil supply passage for the shaft member bearing 19). Here, since the drain oil passage 4e rotates integrally with the tubular member 4, the lubricating oil is also discharged from the drain oil passage 4e at about the same circumferential speed as the tubular member 4. The lubricating oil reaches the shaft member bearing 19 along the inner wall of the tubular member and lubricates the shaft member bearing 19. Since the outer ring of the shaft member bearing 19 rotates integrally with the tubular member 4, when the shaft member bearing 19 is lubricated by the lubricating oil, the outer ring of the shaft member bearing 19 comes into contact with the lubricating oil at a speed close to that of the lubricating oil. Stirring resistance is very low.

The lubricating oil that has passed through the shaft member bearing 19 enters the space B, and then enters the space C from the space B via the axial oil discharge passage 4 f of the tubular member 4. From the space C, the lubricating oil returns to the external tank (not shown) via the external discharge passage 23.

Although the present invention has been described in detail above with reference to the exemplary embodiments, the present exemplary embodiments should not be limited to the above-described exemplary embodiments, but can be appropriately improved and changed within the scope of the present invention. Of course. For example, the pump for pumping the lubricating oil is not limited to the trochoid pump, but may be a vane type or a gear type.

[0021]

【The invention's effect】

 As described above, according to the toroidal type continuously variable transmission of the present invention, the shaft member bearing is provided between the tubular member and the shaft member, and the tubular member bearing includes the housing and the tubular member. Since it is provided between the two bearings, it is not necessary to arrange both bearings side by side in the axial direction, and the axial length is shortened. Further, since the oil supply passage for the bearing member rotates integrally with the tubular member, the lubricating oil supplied from the oil supply passage does not resist the rotation of the shaft member bearing.

[Brief description of drawings]

FIG. 1 is a partial cross-sectional view of a toroidal type continuously variable transmission according to the present invention.

FIG. 2 is an enlarged view of the left side portion of the embodiment shown in FIG.

FIG. 3 is an axial sectional view of a toroidal type continuously variable transmission according to the related art.

[Explanation of symbols]

 4 Tubular member 4e Oil drainage passage (oil supply passage for shaft member bearing) 5 Tubular member bearing 12 Input disk 14 Output disk 15 Shaft member 19 Shaft member bearing 20 Trochoid pump rotating part

Continued Front Page (72) Inventor Hiroyuki Ito 2-14-15 Fujigaoka, Fujisawa City, Kanagawa Prefecture

Claims (1)

[Scope of utility model registration request] 1. A housing, an input disc, an output disc, and a power is transmitted from one of the input disc and the output disc to the other by abutting against the input disc and the output disc and rolling. Roller means, a shaft member connected to any one of the input side disc and the output side disc to transmit power, and provided so as to include the shaft member, the input side disc and the output side disc And a tubular member that is coupled to the other of the two and transmits power, and a shaft member bearing that is provided between the tubular member and the shaft member and that rotatably supports the shaft member with respect to the tubular member. A tubular member bearing that is provided between the housing and the tubular member and rotatably supports the tubular member with respect to the housing; and a pumping unit that pumps lubricating oil that lubricates the shaft member bearing. The pumping means comprises a pumping section for pumping the lubricating oil and an oil supply passage connected to the pumping section for supplying the pumped lubricating oil to the bearing, and the oil supply passage includes the tubular member. Toroidal type continuously variable transmission that rotates integrally.