JP2580273Y2 - Toroidal type continuously variable transmission - Google Patents

Description

[Detailed description of the invention]

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a toroidal type continuously variable transmission used for a vehicle or the like.

[0002]

2. Description of the Related Art A toroidal type continuously variable transmission is known as a transmission capable of changing a speed ratio continuously. Such a toroidal-type continuously variable transmission is, for example,
No. 158249. FIG.
1 is an axial sectional view of a toroidal-type continuously variable transmission described in 2-158249. The configuration and operation of a toroidal-type continuously variable transmission according to the related art will be described below with reference to FIG. An input shaft 102 is provided in a housing 101.
Extends. An input shaft 102 whose right end is connected to a rotating part of an engine (not shown) is rotatably supported by a housing 101 by bearings 103 and 104. The input shaft 102 has a disk portion 10 near the bearing 104.
5 is mounted coaxially and immovable in the axial direction, so that the input shaft 102 and the disk portion 105 rotate integrally. The input disk 107 is provided in parallel with the disk portion 105, and a loading cam 106 is provided between the input disk 107 and the disk portion 105. The loading cam 106 presses the input disk 107 against the disk portion 105 with an appropriate force, and a predetermined force is applied between the loading cam 106 and the disk portion 105 and between the loading cam 106 and the input disk 107, respectively. Frictional force is generated, and therefore, the frictional force
The input disk 107 rotates integrally with the input disk 05.

An output disk 109 is provided facing the input disk 107, and a power roller 108 is provided between the input disk 107 and the output disk 109 with oil interposed therebetween so as to be rotatable. It is provided in. 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 110 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 around an axis perpendicular to the paper surface by a support mechanism (not shown), and changes the contact position with respect to both disks. Input shaft 10
2 The housing 101 near the left end 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 corresponding to the supply passage 112 is provided at the left end of the input shaft 102, and the oil supply passage 114 connects the inner end of the oil passage 113 to the outer periphery of the input shaft 102. Is provided. The oil supply passage 114 is provided for the bearing 10.
3 and the space defined between 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 part of the engine (not shown) is applied to the disk part 1 via the input shaft 102.
05. The torque transmitted to the disc 105 is applied to the input disc 10 via the loading cam 106.
7 is transmitted.

[0005] Input disk 107 and power roller 108
Therefore, oil is interposed between the input disk 107 and the power roller 108, so that the shear force of the oil acts on the input disk 107 as the input disk 107 rotates.
Due to the action of the shearing force, the power roller 108 rotates with almost no slip relative to the input disk 107, and the rotational force transmitted to the input disk is transmitted to the power roller 108. Similarly, the rotational force is transmitted from the power roller 108 to the output disk 109, and further transmitted from the output disk 109 to the axle (not shown) via the gear 110. Power roller 1
When 08 rotates around an axis perpendicular to the paper surface, the rotation speed of the output disk 109 with respect to the rotation speed of the input disk 107 changes according to the contact position. As a result, a continuously variable transmission is achieved.

[0006]

The bearing 103 for supporting the input shaft 102 and the bearing 111 for supporting the output disk 109 are lubricated by lubricating oil supplied from an 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 oil supply passage 114 is
At the speed of the inner ring 3, the lubricating oil is discharged in the tangential direction. Therefore, the lubricating oil does not cause any resistance when the bearing 103 rotates. However, as long as the output disk 109 has a rotation speed different from that of the input shaft 102 unless the gear ratio is 1 to 1, the lubricating oil discharged from the oil drain passage 114 is changed according to the speed difference when the bearing 111 rotates. Resistance (stirring resistance). 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 provided 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 mounting design of the continuously variable transmission. The present invention is directed to a toroidal-type continuously variable transmission that can prevent transmission of lubricating oil against rotation of a bearing, improve transmission efficiency of the transmission, and reduce the axial length of the entire transmission. The purpose is to provide a machine.

[0007]

SUMMARY OF THE INVENTION A toroidal-type continuously variable transmission according to the present invention includes a housing, an input disk, an output disk, and an input disk which is brought into contact with the input disk by rolling. A disk and roller means for transmitting power from one of the output disks to the other; a shaft member connected to the output disk for transmitting power; and an input disk provided to include the shaft member and comprising the shaft member. A tubular member connected to a loading cam connected to a torque cam to transmit power, and a tubular member provided between the tubular member and the shaft member to rotatably support the shaft member with respect to the tubular member. A shaft member bearing; provided between the housing and the tubular member in the axial direction near the shaft member bearing, and rotatably supporting the tubular member with respect to the housing. A tubular member bearing that; comprising a pumping means for pumping the lubricating oil for lubricating the shaft member bearing and the tubular member bearing provided on the tubular member. The pumping means includes a pumping section for pumping the lubricating oil, and an oil supply passage connected to the pumping section and supplying the lubricating oil fed to the shaft member bearing and the tubular member bearing. Rotates integrally with the tubular member.

[0008]

The lubricating oil is supplied to both bearings from the tubular member rotating around the shaft member, so that the lubricating oil hardly causes rotation resistance. Further, since the shaft member bearing and the tubular member bearing are arranged close to each other in the axial direction of the shaft member and the tubular member, the axial length of the entire transmission can be reduced.

[0009]

Embodiments 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 has a left half 1a and a right half 1
b. The configuration of the toroidal type continuously variable transmission according to the present invention will be described from the input side. Spline part 2a at the center
Is connected to a power source (not shown) by its spline portion 2a. The disk portion 2 is provided with several bolt holes 2b at equal intervals near the outer periphery. A tubular member 4 is provided adjacent to and coaxial with the disk portion 2.
The tubular member 4 has a configuration in which a flange portion 4a, a large circular tube portion 4b, and a small circular tube portion 4c are connected in series in the axial direction. Several female threads are provided in the flange portion 4a at positions corresponding to the bolt holes 2b of the disk portion 2, and the disk portion 2 and the tubular member 4 are fastened by the bolts 3.

The outer periphery of the large tube portion 4b of the tubular member 4 is rotated by the tubular member bearing 5 with respect to the housing 1, and the outer periphery of the small tube portion 4c of the tubular member 4 is rotated by the bearing 6 with respect to the housing 1. It is freely supported. Serrations 4d are formed on the inner periphery of the small circular tube portion 4c. Small pipe section 4
A pressing member 9 having a configuration coaxially connected to the circular plate 9a and the circular tube 9b is provided adjacent to c. A serration 9c is provided on the outer circumference of the circular tube 9b, and the tubular member 4 can move in the axial direction by engaging the serration 4d with the serration 9c of the pressing member 9, but can transmit the rotational force. It is connected to the pressing member 9. Between the pressing member 9 and the free end of the small circular tube portion 4c of the tubular member 4,
A spacer 7 and a disc spring 8 are provided, and the disc spring 8 urges the pressing member 9 and the tubular member 4 in directions separated from each other in the axial direction.

The pressing member 9 has an input disk 12 with a loading roller 11 supported by a retainer 10 therebetween.
Is adjacent to The input disk 12 has a substantially conical shape, has an outer slope formed in a toroidal shape, and has an opening 12a passing therethrough in the axial direction. The loading roller 11 comes into contact with both the pressing member 9 and the input disk 12, and presses the input disk 12 against the power roller assembly 13 by the relative rotation of the pressing member 9 and the input disk 12. .

An output disk 14 having the same outer slope is provided opposite 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 includes a trunnion 13a, a shaft 13b, a bearing 1
3c 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 provided with the bearing 1 with respect to the trunnion 13a.
3c, and is rotatable around the 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 includes:
The power roller assembly 13 is rotated around an axis perpendicular to the paper surface. 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 diameter of the contact portion between the roller portion 13d and the input disk 12 and the effective portion of the contact portion between the roller portion 13d and the output disk 14 become smaller if one decreases. Changes to increase.

The output disk 14 has an opening 14a extending in the axial direction and penetrating therethrough, and a serration portion 14b is formed on the inner periphery of the opening 14a. The 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 on the shaft member 15 via a bearing 16, and the pressing member 9 is supported on 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 thread 15c is engraved on the left end of the shaft member 15, and a preload nut 18 is screwed into the male thread 15c. The outer periphery of the preload nut 18 is provided via a shaft member bearing 19,
The tubular member 4 is supported on the inner circumference of the great circular tube portion 4b. 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 transmission device (not shown) via the spline portion 15b. The tubular member bearing 5 and the shaft member bearing 19 have an inner and outer relationship in the radial direction, and are close to each other in the axial direction.

Next, a 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 portion of the embodiment shown in FIG. FIG.
, A serrated portion 4d is provided on the outer periphery of the small circular tube portion 4c of the tubular member 4 adjacent to the bearing 6. A trochoid pump rotating part 20 is provided in a cavity 1c having an elliptical cross section as viewed from the axial direction, which is formed radially outward of the small circular tube part 4c and at the end of the right half part 1b of the housing 1. I have. The rotating portion 20 has a disk shape, and a serration portion 20 a provided on the inner periphery is engaged with a serration portion 4 d of the tubular member 4. Therefore, the rotating part 20 rotates together with the tubular member 4. A pump inner space is formed by the left half 1a of the housing 1 and the cavity 1c. Reference numeral 20b denotes a space where the oil in the pump rotating section is pushed out.

A lubricating oil supply passage (not shown) is provided in the right half 1b of the housing 1, and a lubricating oil discharge passage 1d is provided in the left half 1a. Lubricating oil discharge passage 1d
Communicates with an oil drain passage 4e that penetrates the small circular pipe portion 4c in the radial direction. Although not shown in the drawing, the oil drain passage 4e
The lubricating oil discharge passage 1d has a radially inner end communicating with an annular groove 4g extending in the outer circumferential direction of the small circular tube portion 4c. Therefore, the lubricating oil passage 1d always communicates with the oil drain passage 4e at any position. The oil drain passage 4 e 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 disk portion 2 is provided outside the space A with the shaft member bearing 19 therebetween. A tubular lid member 21 having one end closed is provided adjacent to the disk 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. Space B
Communicates with the space C via an axial oil drain passage 4f that penetrates the great circular tube portion 4b of the tubular member 4 in the axial direction. Space C
Is defined by a left half 1a of the housing 1, a tubular member 4, and a tubular member bearing 5. The space C further communicates with an external tank (not shown) via an external discharge passage 23. A seal 24 is provided adjacent to the tubular member bearing 5,
Leakage of oil lubricating the tubular member bearing 5 is prevented.

Next, the operation of the toroidal type continuously variable transmission according to the present invention will be described below. In FIG. 1, rotational force is transmitted to a tubular member 4 from a rotating part of an engine (not shown) via a spline part 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 through the roller portion 13d of the power roller assembly 13.
Is rotated. In this case, the effective diameter of the contact portion between the input disk 11 and the output disk 14 in the roller portion 13d of the power roller assembly 13 shown in FIG. 1 is substantially the same, so that the gear ratio is 1: 1. Has become. From this state, the power roller assembly 1 shown in FIG.
3 rotates counterclockwise, and the lower power roller assembly 1
3 rotates clockwise, the effective diameter of the contact portion between the power roller assembly 13 and the input disk 12 decreases, and at the same time, the effective diameter of the contact portion between the power roller assembly 13 and the output disk 14 increases. Therefore, the gear ratio changes steplessly toward the deceleration side. Clearly, when the power roller assemblies 13 rotate in opposite directions, respectively.
The gear ratio changes steplessly to the increasing side. When the output disk 14 rotates, the shaft member 15 is rotated, and a rotational force is transmitted to a power transmission device (not shown) via the spline portion 15b.

In FIG. 2, when the tubular member 4 rotates, the trochoid pump rotating section 20 rotates, whereby the lubricating oil is pressure-fed from a lubricating oil supply passage (not shown) to the lubricating oil discharge passage 1d. The lubricating oil fed by pressure is supplied to the space A via an oil discharge passage 4e (which becomes an oil supply passage for the shaft member bearing 19).
Is discharged. Here, since the oil discharge passage 4 e rotates integrally with the tubular member 4, the lubricating oil is also discharged from the oil discharge passage 4 e at substantially the same circumferential speed as the tubular member 4. This 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 with lubricating oil,
Since it comes into contact with the lubricating oil at a speed close to the lubricating oil, the stirring resistance in the shaft member bearing 19 is extremely low. The situation is the same for the tubular member bearing 5, the inner ring of which is the tubular member 4.
And the agitation resistance in the bearing 5 is also very small.

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

As described above, the present invention has been described in detail with reference to the embodiments. However, the present embodiment is not limited to the above-described embodiments, and can be appropriately modified 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]

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 is provided between the housing and the housing. The axial length of the entire transmission is reduced because it is provided between the tubular members and is close to each other in the axial direction. Further, since the oil supply passage to the shaft member bearing and the tubular member bearing rotates integrally with the tubular member, the lubricating oil supplied from the oil supply passage does not cause resistance when the shaft member bearing rotates.

[Brief description of the drawings]

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

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

FIG. 3 is an axial sectional view of a conventional toroidal-type continuously variable transmission.

[Explanation of symbols]

 Reference Signs List 4 tubular member 4e oil drain 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

──────────────────────────────────────────────────続 き Continuation of the front page (56) References JP-A-2-261950 (JP, A) (58) Fields investigated (Int. Cl. ⁶ , DB name) F16H 15 / 38,57 / 04

Claims (1)

(57) [Scope of request for utility model registration] 1. A housing (1), an input disk (12), an output disk (14), and the input disk and the output disk are brought into contact with and rolled by the input disk and the output disk. Roller means (11) for transmitting power from one side to the other; a shaft member (15) connected to the output side disk for transmitting power; and the input side disk provided to include the shaft member. A tubular member (4) connected to a loading cam connected to a torque cam to transmit power, and a tubular member (4) provided between the tubular member and the shaft member, wherein the shaft member is rotatable with respect to the tubular member. Shaft bearing (1)
9) a tubular member bearing (5) provided between the housing and the tubular member in the axial direction near the shaft member bearing and rotatably supporting the tubular member with respect to the housing; And a pumping means provided on the tubular member for pumping the shaft member bearing and lubricating oil for lubricating the tubular member bearing, the pumping means being connected to the pumping section (20) for pumping the lubricating oil, and to the pumping section. Oil supply passages (4d, 4d) for supplying the lubricating oil fed and supplied to the shaft member bearing and the tubular member bearing.
e) wherein the oil supply passage rotates integrally with the tubular member.