JPH0442596Y2 - - Google Patents

Description

[Detailed description of the invention] (Field of industrial application) The present invention relates to a friction-driven continuously variable transmission, and more specifically to a continuously variable transmission that transmits engine output to drive wheels in a vehicle with a continuously variable gear ratio. Regarding improvements.

(Prior Art) One type of friction-driven continuously variable transmission is one that outputs the rotational force changed by a transmission device provided on an input shaft to an output shaft parallel to the input shaft via a torque transmission device. be. When using a toroidal type transmission, the input disk is loosely fitted on the input shaft, and the output disk is loosely fitted on the output shaft.
A traction roller is placed between both disks.
A pressure device such as a cam roller is provided between the input shaft and the input disk in order to generate a frictional force between the two disks and the traction roller. When a rotational input is applied to the input shaft, the pressurizing device presses the input/output disk and the traction roller, thereby transmitting torque. At this time, the bearings that support the output disk and the end of the input shaft within the housing are subject to high speed rotation and high loads. A conventional pressurizing device for a toroidal transmission has a cam roller disposed between an input disk having cam surfaces facing each other and a cam plate on an input shaft, and presses the input disk with a force corresponding to input torque. The pressed input disk frictionally engages with the traction roller and the output disk to transmit rotational torque to the output disk at a predetermined gear ratio. At this time, the output disk receives a high load in the opposite direction to the load on the input shaft, so the bearings that support the output disk and input shaft in the housing must be used independently for the input shaft and output disk. need to be placed.

(Problem to be solved by the invention) In the friction-driven continuously variable transmission described above, the two bearings that respectively support the output disk and the input shaft in the housing are attached to the housing that surrounds the tip of the input shaft. They are typically located adjacently within the recess. In this case, the bearings are lubricated by lubricating oil that is forcefully lubricated between both bearings. The lubricating oil introduced between both bearings flows while lubricating the inside of the bearings, and flows out to the outside of both bearings. The lubricating oil that has flowed through the bearing that receives the output disk returns to the oil reservoir in the housing, but the lubricating oil that has flowed through the bearing that receives the other input shaft is returned to the space formed between that bearing and the housing. It gets contained.
The lubricating oil sealed in this space becomes high pressure, passes through the bearing again, and returns to the oil reservoir. When the return flow rate of lubricating oil through the oil pan increases, bearing rotational resistance increases and the transmission efficiency of the transmission decreases, and in some cases, the transmission efficiency decreases by 2 to 3%. It will cause it.

The purpose of the present invention is to improve transmission efficiency in a friction-driven continuously variable transmission that performs speed change operations at high speeds and high loads.

(Means for Solving the Problems) The continuously variable transmission of the present invention has a long input shaft to which a rotational input is applied from one end and a different axis from the input shaft, and provides a rotational output to a load. an output shaft, a continuously variable transmission ratio transmission means disposed on the input shaft for friction-driven transmission of the rotational input to the input shaft through rolling of rolling elements, and a rotational force changed by the transmission means. a transmission means for transmitting data to an output shaft; a housing that includes the transmission means and the transmission means and supports both shafts so that the one end of the input shaft and the output end of the output shaft extend from the inside; and an input shaft. a first bearing means whose other end is supported within the housing and defines a first chamber between the first bearing means and the housing; a second bearing means defining a second chamber for storing lubricating oil between the first and second bearing means; a lubricating means for supplying the lubricating oil in the second chamber between the first and second bearing means; The lubricating oil is further provided with communication passage means that allows the lubricating oil to flow further into the second chamber. By providing a lubricating oil communication path that communicates between the first chamber and the second chamber, a lubricating oil flow path is secured. Therefore,
High-pressure lubricating oil no longer flows back inside the bearing, reducing fluid agitation resistance and improving the transmission efficiency of the transmission.

(Example) An example of the present invention will be described below with reference to the drawings.

The long input shaft 4 has one end directly connected to an output shaft of an engine (not shown), and the other end extends into the housing 10 . housing 10
defines a chamber 1 inside, and an input shaft 4 is located inside the chamber 1.
extends into the chamber 1 and is rotatably supported by a ball bearing 37 and a bearing device C at both ends of the chamber 1. A pressure device A and a transmission B, which will be described later, are arranged on the input shaft 4 between the ball bearing 37 and the bearing device C.
Both ends of the ball bearing 37 are sealed by seals 8 and 9 to prevent leakage of lubricating oil from the chamber 1.

An output shaft 6 is parallel to the bottom of the input shaft 4.
It extends into the housing 10 from the opposite side. One end of the output shaft 6 is connected to a load such as a wheel (not shown). The other end of the output shaft 6 is connected to the housing 10
It extends into the chamber 1, and its tip is supported on the housing via a sleeve or the like. Further, the output shaft 6 is rotatably supported by a ball bearing 36 at the end of the housing 10, and a seal 43 is provided on the outside thereof.
is placed to prevent lubricating oil from leaking. A clutch device D, which will be described later in connection with the pressurizing device A and the transmission B, is arranged on the output shaft 6.

The pressurizing device A includes a cam plate 18 that rotates integrally with the input shaft 4, and an input disk 11 facing the cam plate 18.
It consists of a rear surface and a cam device 19. A cam surface is formed on the rear surface of the cam plate 18 and the input disk 11, and a cam device 19 such as a roller or ball rolls on this cam surface to press the input disk 11 according to input torque.

The transmission B includes an input disk 11, a traction roller 15, a trunnion 17, and an output disk 1.
It consists of 3 mag. A toroidal cavity is formed between the facing surfaces of the input disk 11 and the output disk 13, and a plurality of traction rollers 15 are arranged axially symmetrically within this cavity.
A sleeve 14 extends from the rear surface of the output disk 13 to surround the input shaft 4, and is rotatably supported in the housing 10 by a needle bearing on the input shaft 4 at one end and a bearing device C at the other end.

Since the output disk 13 is not displaced in the axial direction,
When the input disk 11 is pressed by the pressure device, a frictional force is generated between the two disks 11, 13 and the traction roller 15, and rotational force is transmitted from the input disk 11 to the output disk 13. The traction roller 15 is rotatably supported by a trunnion 17. Further, the trunnion 17 is associated with a control device (not shown), and is displaced by the control device in a direction perpendicular to the input shaft 4 for speed change, and as a result, the trunnion 17 tilts between the disks 11 and 13 to change the speed ratio.

Two gears 23 and 25 are formed on the sleeve 14 for transmitting the rotational force transmitted to the output disk 13 to the clutch device D on the output shaft 6. Gear 23 is a forward gear, and gear 25 is a reverse gear.

The bearing device C that supports the input shaft 4 and the end of the sleeve 14 includes a first ball bearing 21 that supports the input shaft 4 and a second ball bearing 22 that supports the sleeve 14. Both ball bearings 21 and 22 are attached to the housing 10
are supported adjacently in a recess within with a spacer 20 interposed therebetween;
A chamber 32 is defined between the first ball bearing 21 and the housing 10. The inner ring of the first ball bearing 21 is supported by a sleeve 26 on the end of the input shaft 4 so as not to be displaced in the axial direction. The sleeve 26 is connected to the input shaft 4
It is fixed by an adjustment nut 30 that screws into a fine adjustment screw 29 formed at the end. Adjustment nut 3
0 finely adjusts the axial position of the input shaft 4 and displaces the position of the cam plate 18 of the pressurizing device A depending on the screwing position with the fine adjustment screw 29. Therefore, the pressurization applied to the cam device A and the transmission can be finely adjusted.

The lubricating means introduces lubricating oil from the end of the input shaft 4 through the oil inlet 33 on the housing 10 . Lubricating oil is forcibly circulated to the oil path 31. Lubricating oil is released from the oil passage 31 through the oil outlet 34 between the first ball bearing 21 and the second ball bearing 22. The released lubricating oil flows through both ball bearings 21 and 22 and enters chamber 32, respectively.
and is discharged into chamber 1.

The lubricating oil discharged into the chamber 1 returns directly to the oil reservoir 35, but the lubricating oil discharged into the chamber 32 flows through the communication passage 50 bored in the housing 10 as shown in FIG.
It returns to the oil sump 35 in the chamber 1 through the oil tank. Communication path 5
0 is provided below both ball bearings 21 and 22, so that the lubricating oil that has flowed into chamber 32 naturally returns to chamber 1. Although the communication path 50 is formed as a groove on the housing 10 in this embodiment, it may be formed as a groove on the both ball bearings 21 and 22 side.

Clutch device D includes a first clutch 51 that transmits the rotational force on the output disk 13 side to the output shaft 6, and a second clutch 52 that transmits the rotational force on the input shaft 4 side to the output shaft 6.

The first clutch 52 consists of a gear 28 meshing with the gear 23, a clutch housing 53, and a pressure plate 29. gear 28
is rotatably fitted onto the output shaft 6, and
It has a cylindrical portion extending along the output shaft 6, and a plurality of friction plates extend radially outward from the cylindrical portion. On the other hand, the clutch housing 53 is connected to the gear 28
It has a clutch plate that covers the cylindrical portion of the friction plate and extends between both sides of the friction plate. The clutch plate is actuated by a pressure plate 29 within the clutch housing 53, and engages and disengages from the friction plate of the gear 28.

The pressure plate 29 is connected to the oil passage 4 in the output shaft 6.
1 through the oil outlet 43.

On the other hand, the second clutch 52 has the same structure as the first clutch 51, and is composed of a gear 40, a clutch housing 54, and a pressure plate 39. The gear 40 meshes with teeth on the outer circumference of the cam plate 18 via an idle gear 46, and is rotatably fitted onto the output shaft 6. The gear 40 also has a plurality of friction plates in its cylindrical portion, facing a clutch plate extending from the clutch housing 54. The engagement and separation between the clutch plate and the friction plate is controlled by a pressure plate 39.
The pressure plate 39 is connected to the oil passage 42 in the output shaft 6.
It is controlled by the oil pressure that passes through the oil outlet 47.

A reversing gear 27 is further disposed on the output shaft 6 so that it can be displaced in the axial direction but rotates integrally with the output shaft 6. The gear 27 is displaced in the axial direction and meshes with the gear 25 on the output disk 13 via an idle gear (not shown).

The operation of the continuously variable transmission having the above configuration will be explained.

When engine output is applied to the input shaft 4, the input/output disks 11, 13 and the traction roller 15 are pressed against each other by the pressurizing device A, and the rotational force is transmitted to the output disk 13 at a predetermined gear ratio by frictional force. do. At this time, if both the first clutch 51 and the second clutch 52 are disengaged and the gears 27 and 25 are not engaged, no rotational force is transmitted to the output shaft 6.

Input shaft 4 and output disk 13 or sleeve 14
are supported while rotating on the first and second ball bearings 21 and 22, respectively, while receiving forces that separate them from each other in the axial direction. At this time, the first and second ball bearings 21,
22 operates smoothly with the lubricating oil coming out from the oil outlet 34.

Until the speed of the vehicle reaches a predetermined value from low speed to high speed, the rotational force is transferred to the output shaft 6 via the first clutch 51.
transmitted to. When the vehicle speed becomes high and exceeds a predetermined value, the rotational force is transmitted to the output shaft 6 via the second clutch 52. When the vehicle is traveling backwards, both clutches 51 and 52 are disengaged, and rotational force is transmitted from gear 25 to gear 27 via the idle gear.

(Effects of the invention) In order to improve the lubrication efficiency of the bearing means that supports the input shaft and output disk in the housing, which are subjected to high speed rotation and high load, the invention arranges two bearings adjacent to each other and provides a communication path for lubricating oil. Therefore, it is possible to provide a friction drive type continuously variable transmission having a simple configuration and high transmission efficiency.

[Brief explanation of the drawing]

FIG. 1 is a side sectional view of a friction-driven continuously variable transmission showing an embodiment of the present invention, and FIG. 2 is a sectional view taken along the line - in FIG. 1. Explanation of symbols of main parts, 4... Input shaft, B...
Transmission device, 6...output shaft, C...bearing device, A...
...pressure device, D...clutch device, 21...first
Ball bearing, 22...Second ball bearing, 23...Gear, 3
1...Oil passage, 33...Oil inlet, 35...Oil sump,
51...first clutch, 52...second clutch.

Claims (1)

[Claims for Utility Model Registration] 1. An input shaft whose one end is connected to a drive source, an output shaft that transmits power to a driven member, and an input shaft that has a toroidal surface and receives the power transmitted from the input shaft. a disk; an output disk having a toroidal surface and transmitting power to the output shaft; and a rotatably contacting toroidal surface of each of the input disk and output disk to transmit power between the input disk and the output disk. a toroidal type stepless transmission roller comprising: a transmission roller having a traction surface that rotates; a trunnion that rotatably supports the transmission roller; and a housing that surrounds the input shaft, output shaft, input disk, output disk, transmission roller, and trunnion. In the transmission, the other end of the input shaft is rotatably supported by a first bearing between the input shaft and the housing, so that a first chamber is formed between the housing and the first bearing. and one end of the output disk is rotatably supported by a second bearing disposed adjacent to the first bearing, so that the input shaft and the output shaft are connected between the housing and the housing. , defining a second chamber accommodating the input disk, the output disk, the transmission roller and the trunnion, and provided with lubrication means for supplying lubricating oil within the second chamber to the first and second bearings. between the first and second bearings and the housing;
A toroidal continuously variable transmission characterized by being provided with a lubricating oil passage that allows lubricating oil to flow between the chamber and the second chamber. 2. The toroidal continuously variable transmission according to claim 1, wherein the lubricating oil passage is a groove provided on the inner surface of the housing.