JPS62283256A - Lubricating device for troidal-shaped continuously variable transmission - Google Patents

Abstract

PURPOSE:To eliminate the useless consumption of traction oil by turning a trunnion together with power rollers as the speed change ratio varies and lubricating the content part by the traction oil. CONSTITUTION:Traction oil is supplied to the contact part between a power roller 24 and input and output discs 21 and 22 from a lubrication hole 28b formed at the upper edge part of a trunnion 28. When the contact part between the power rollers 23 and 24 and the input and output discs 21 and 22 changes as the speed change ratio varies, the trunnions 27 and 28 turn integrally with the power rollers 23 and 24. Therefore, when traction oil is discharged from the lubrication holes 27c and 28b, a necessary quantity of traction oil can be supplied into the part where lubrication is necessary, and useless consumption of oil can be prevented.

Description

Detailed Description of the Invention 3. Detailed Description of the Invention Field of Industrial Application The present invention relates to a lubricating device for a toroidal continuously variable transmission, particularly to a lubricating device for supplying traction oil to a traction drive surface. .

Conventional technology and its problems Conventionally, a pair of power rollers is placed in pressure contact between input and output disks arranged opposite each other, and a trunnion that rotatably supports the power roller is rotated in its own axial direction (supporting the power rollers). The input and output discs act on the power roller by operating the power roller in the direction perpendicular to the shaft. Japanese Unexamined Patent Publication No. 58-54262 discloses a toroidal continuously variable transmission that changes the direction of a tangential force and changes the inclination of a power roller by the component of this tangential force, thereby achieving continuously variable speed. It is shown.

In the case of the above-mentioned toroidal continuously variable transmission, if mineral oil such as gear oil or automatic transmission fluid (ATF), which is used in general transmissions, is used as lubricant, the power roller, input and output Since sufficient power cannot be transmitted between the disc and the disc, traction oil with a traction coefficient suitable for traction drive is used.

When the contact portion between the power roller and the input and output disks is to be slid with traction oil, the traction oil is usually jetted out from a part called a post fixed to the casing. However, since the contact area between the power roller and the input and output discs changes depending on the gear ratio, spouting traction oil from a post installed at a fixed location as described above does not necessarily ensure that the contact area is properly gliding. Not done. As a result, an oil film peels off at the contact area between the power roller and the input and output disks.
There is a risk that the power transmission efficiency will be reduced and the drive surface will be worn out, and there is also the problem that traction oil is wasted.

Purpose of the Invention The present invention has been made in view of such conventional problems.
The purpose is to provide a /rJI shoulder device for a toroidal continuously variable transmission that can efficiently supply traction oil to the contact area between the power roller and the input and output disks even when the gear ratio changes.

Structure of the Invention In order to achieve the above object, the present invention includes input and output disks that are arranged opposite to each other, a pair of power rollers that are placed in pressure contact between the input and output disks, and a power roller that is connected to the input and output disks through a support shaft. A toroidal type continuously variable transmission that is rotatably supported by a trunnion, and a pair of trunnions that are movable in the axial direction and rotatable around its own axis, and that the gear ratio is variable by operating the trunnions in the axial direction. In the trunnion, a lubrication hole is formed inside the trunnion to guide traction oil to the contact area between the power roller and the output disk.

DESCRIPTION OF EMBODIMENTS The first page shows an example of a toroidal continuously variable transmission according to the present invention. This continuously variable transmission is roughly composed of a human power shaft 10, a toroidal transmission section 20, a loading cam device 30, a starting clutch 40, an output shaft 50, a forward/reverse switching mechanism 51, a differential device 60, and a direct coupling clutch 70. is covered by a casing 1°2.3.

A crankshaft 4 of the engine is connected to an input shaft 1O via a flywheel 5 and a torsional damper 6 for absorbing engine torque fluctuations. The boss portion 6a of the torsional damper 6 is also spline engaged with a gear type oil pump 7 for circulating mineral oil, thereby driving the oil pump 7. Two bearings 11 and 12 are arranged adjacent to each other on the left side of the oil pump 7. The bearing 11 supports the thrust load acting on the input shaft 10 in the left direction in the figure, and the bearing 12 supports the toroidal transmission section 20, which will be described later. The thrust load acting on the output disk 22 in the right direction in the figure is supported.

The toroidal transmission section 20 includes an input disk 21 and an output disk 22 that are rotatably arranged on the input shaft 1O, and an input disk 2111 that is placed in pressure contact between the opposing annular surfaces 21a and 22a of both disks 21.22. Power roller 23.
The input disk 21 and the output disk 22 rotate in opposite directions as the power rollers 23 and 24 move. The speed change control of the toroidal transmission section 20 is performed by operating the trunnion 27.28, which supports the power rollers 23, 24 via the support shafts 25.26, in a direction perpendicular to the axis of the input shaft IO, and the speed change control mechanism The specific structure of is shown in FIG.

Note that the upper half of the input shaft IO in FIG. 1 shows a low speed ratio state, and the lower half shows a high speed ratio state.

The input shaft 1 is connected to the input disk 21 at the shaft end of the input shaft 10.
A loading cam device 30 is provided that applies a thrust force (thrust load) proportional to zero input torque. The loading cam device 30 includes a cam surface 21b formed on the back surface of the input disk 21 and a cam surface 31 formed on the side surface of the cam disk 31 spline-coupled to the input shaft 10.
a, and a cam roller 32 which is disposed removably between both cam surfaces 21b and 31a, and as the input torque increases, the power roller 23, 24 and the annular surfaces 21a, 22
By increasing the contact pressure between a and a, power is transmitted without slipping. A nut 33 is screwed onto the end of the input shaft 10, and this nut 33 presses and supports the back surface of the cam disc 31 via a disc spring 34. The L spring 34 applies contact pressure between the cam roller 32 and the cam surfaces 21b and 31a, and also provides contact pressure between the power roller 23, 24 and the annular surface 21a.
, 22a is applied. A direct drive gear 31b is integrally formed on the outer periphery of the cam disc 31, and a gear type oil pump 35 for circulating traction oil is provided at the left end of the input shaft 10.

A starting clutch 40 consisting of a wet multi-disc clutch is arranged between the toroidal transmission section 20 and the bearings 11.12, and a clutch drum 41 of this starting clutch 40 is rotatably supported on the input shaft 10 and an output disc The right end portion of the boss member 42 is supported by the bearing 12. The clutch hub 44, which is connected and disconnected via the clutch drum 41 and the clutch slope 43, is connected to the boss member 42.
It is connected to a drive gear 45 rotatably supported above.

A driven gear 47 that meshes with the drive gear 45 is spline-coupled to a counter shaft 46 arranged parallel to the input shaft IO. Furthermore, a forward drive gear 48 and a reverse drive gear 49 are integrally formed on the counter shaft 46.

The output shaft 50 is also arranged parallel to the input shaft 10, and a forward/reverse switching mechanism 51 is provided on the output shaft 50. The forward/reverse switching mechanism 51 includes a forward driven gear 52 that meshes with the forward drive gear 48, a reverse driven gear 54 that meshes with the reverse drive gear 49 via an idler gear (not shown), and a spline hub 55. Switching sleeve 56
By operating the switching sleeve 56 in the axial direction, forward and backward switching is performed. An output gear 57 is integrally formed on the right end of the output shaft 50.
7 meshes with a ring gear 61 of a differential device 60 and transmits power to an axle 62.

The left end of the output shaft 50 is extended to the left by approximately the same length as the input shaft 1O, and this extension includes the input disk 2.
A direct coupling clutch 70 is disposed at a position corresponding to 1. The clutch drum 71 of the direct coupling clutch 70 is connected to the output shaft 50
This clutch drum 71
and a clutch hub 73 that is connected and disconnected via a clutch slope 72
is coupled to a directly coupled driven gear 74. Directly connected driven gear 7
4 is rotatable with respect to the output shaft 50 and meshes with a direct drive gear 31b formed integrally with the cam disk 31. Note that since Figure 1 is a developed cross-sectional view, both gears 3
Although 1b and 74 are separated, they actually mesh.

In addition, the power rollers 23 and 24 of the toroidal transmission section 20
is actually close to the output shaft 50, as shown by the two-dot chain line in FIG.

A chamber 80 that accommodates the toroidal transmission section 20 and the direct coupling cruft 70, and a chamber 81 that accommodates components such as the bearing IL1'2, the forward/reverse switching mechanism 51, and the differential device 60.
The compartment 8 is separated by a partition wall 2a provided in the casing 2, and the compartment 8 is separated by oil seals 82, 83, 84.
Oil leakage between 0.81 and 200 mm is prevented. And bearing 1
1.12 and the forward/reverse switching mechanism 51 are lubricated with mineral oil discharged by the oil pump 7, and the toroidal transmission section 20 and direct clutch 70 are lubricated by the oil pump 3.
/I21 is slipped by the traction oil discharged by 5. In other words, the bearing 11 whose friction loss is to be reduced as much as possible,
12 and the gear mechanism use mineral oil such as /12I gear oil with excellent lubricity and ATF, and traction oil with a high traction coefficient is used in the toroidal transmission section 20 that performs traction drive. ,12
It is possible to reduce loss of power of the gear mechanism and the gear mechanism, and to improve the power transmission efficiency of the toroidal shift mechanism 20.

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

First, when starting, the direct coupling clutch 70 is disconnected, and the starting clutch 40 is gradually engaged to start the vehicle.

As a result, the power of the input shaft 10 is transferred to the toroidal transmission section 20.
, starting clutch 40, drive gear 45, counter shaft 46,
The power is transmitted from the forward/reverse switching mechanism 51 and the output gear 57 to the differential device 60, and is continuously variable through the toroidal transmission section 20. Toroidal transmission section 20
When the speed ratio reaches the maximum speed ratio or its vicinity, the starting clutch 40 is disengaged and the direct coupling clutch 70 is engaged, and the power of the input shaft 10 is transferred to the cam disc 31 and the direct coupling without passing through the toroidal transmission section 20. The power is transmitted from the driven gear 74, the direct coupling clutch 70, and the output gear 57 to the differential device 60, and the power is transmitted at a constant transmission ratio. Therefore, transmission efficiency during high-speed running can be improved.

In FIG. 2, the trunnion 2 of the toroidal transmission section 20
Hydraulic chambers 80 to 83 and pistons 84 to 87 that can freely slide within the hydraulic chambers 80 to 83 are connected to the upper and lower ends of 7.28, and the hydraulic chambers 80 to 83 are connected to the hydraulic chambers 80 to 83 through orifices 88 to 91. The trunnions 27 and 28 can be moved in the axial direction (in the vertical direction in the figure) and rotated about their own axes by supplying the control hydraulic pressures P, , P2. Among the hydraulic chambers, the lower left and upper right, which are opposite to the rotational direction of the input shaft 10 (indicated by the arrow in the figure), are the positive drive side hydraulic chambers 81.82.
, the upper left and lower right on the opposite side are the reverse drive side hydraulic chamber 8.
It is 0.83. In addition, the positive drive side hydraulic chamber 81.8
A communicating hole 8 is provided at the axis of the piston 85, 86 received in the piston 2.
Shaft portions 85b and 86b having shaft portions 5a and 86a are provided in a protruding manner, and these shaft portions 85b and 86b are slidable relative to the casing 2. The communication holes 85a and 86a
IA Namekawa traction oil is led to the control/Ib (mineral oil) supplied to the hydraulic chambers 80 to 83.
is separated from. The traction oil led to one of the communicating holes 85a passes through KR smooth holes 27a and 27b formed inside the trunnion 27 to the power roller 23.
Inside, that is, crank-shaped support shaft 25, thrust bearing 92
, balls 93, needle bearings 94, etc.,
Furthermore, a lubrication hole 27 formed at the upper end of the trunnion 27
Traction oil is supplied from c to the outer circumferential portion of the power roller 23, particularly to the contact portions with the input and output disks 21 and 22. In addition, the traction oil guided to the other communication hole 86a also flows through the 1lf formed inside the trunnion 28.
Ill? The support shaft 26 and the thrust bearing 95 are inserted through the hole 28a.
, the ball 96, the needle hair ring 97, etc., and the power roller 24 and the output disk 21.
22. This prevents heat generation and wear inside the power rollers 23 and 24, and
Power rollers 23 and 24 and input and output disks 21 and 22
The contact area is filled with traction oil. Also,
Even if the contact area between the power rollers 23, 24 and the input and output disks 21, 22 changes as the gear ratio changes, the trunnions 27, 28 rotate integrally with the power rollers 23, 24, so the lubrication hole 27c By pouring out traction oil from , 28b, the necessary amount of traction oil can be supplied to the parts that require lubrication, and no oil is wasted. In particular, as in the embodiment, the a-smooth holes 27c and 28b
If these are formed at the upper ends of the trunnions 27 and 28, respectively, the contact portions can be lubricated most efficiently without requiring large hydraulic pressure.

The speed change control valve 100 includes a pulp body 101 fixed to the upper surface of the casing 2, a sleeve 102 slidably inserted into the valve body lO1, and a sleeve 10.
3rf with spool 120 slidably inserted into 2
It has a J structure. Four boats 103 to 106 are formed in the sleeve 102, and a boat 1 in the center is formed.
03, line pressure PL is introduced from the hydraulic source, and the right-hand side bore 04 is connected to the positive drive side hydraulic chamber 81.03 via an oil passage (not shown).
82, and the port 105 on the left side is connected to i! via an oil passage (not shown). ! It is connected to the drive side hydraulic chambers 80, 83, and the port 106 is a drain boat. A pin 107 is fixed through the right end of the sleeve 102 in the diametrical direction.
The sleeve 102 is connected via this pin 107 to an actuator 110 for speed ratio control, which is made up of a stepping motor or the like.
axially actuated by. That is, a screw shaft 112 is fixed to the rotating shaft 111 of the actuator 11'0, a threaded cylinder 113 that is threadedly engaged with the screw shaft 112 is inserted into the inside of the sleeve 102, and the notch 113a of this screw cylinder 113 is inserted into the sleeve 102. It is fitted with the pin 107 and is locked in a non-rotatable manner. Further, both ends of the pin 107 protrude from the outer surface of the sleeve 102, and the protruding ends abut against the side surface of the valve body 101 and are prevented from rotating.

Therefore, when the rotating shaft 111 of the actuator 110 rotates in either direction, the sleeve 102 and the threaded cylinder 11
3 is prevented from rotating with respect to the pulp body 101 via the pin 107, so that the screw shaft 112 can move forward inside the screw tube 113, and the sleeve 102 and the screw tube 113 can be moved together in the axial direction. .

A spring 121 is interposed between the shaft 107 and the spool 120, and the spring 121 biases the sleeve 102 and the spool 120 in opposite directions. In addition to absorbing the backlash caused by the bank crash with 113, the spool 1
20 is always brought into contact with a presis cam 123 via a swingable bell crank 122. Brisis cam 1 above
23 is connected to the upper end of the left trunnion 27 by a rod 124, so that the brisis cam 123
can rotate together with the trunnion 27 to move the spool 120 forward and backward.

When changing the gear ratio of the toroidal transmission section 20,
The sleeve 102 may be operated in either the left or right direction by rotating the rotating shaft 111 of the actuator 110 in the normal or reverse direction. For example, when the sleeve 102 is moved to the right in the figure, the ports 03.105 are communicated and the line pressure is guided to the reverse drive side hydraulic chamber 80.83, and the forward drive (1st hydraulic pressure chamber 81.82 hydraulic pressure is spool 120 from po eye 04
The water is drained from the drain boat 106 through a communication hole 120a formed in the axis of the drain boat 106. Therefore, the hydraulic pressure in the reverse drive side hydraulic chamber 80.83 becomes high, and the left trunnion 27
moves downward, and the right trunnion 28 moves upward, and the direction of the tangential force applied to the power rollers 23 and 24 changes accordingly.
3 and the trunnion 27 rotate in a counterclockwise direction when viewed from above, and the power roller 24 and trunnion 28 on the right side rotate in a clockwise direction when viewed from above. That is, the toroidal transmission section 20 is shifted to the lower speed ratio side. The brisis cam 123, which rotates integrally with the left trunnion 27, also rotates counterclockwise, and the spool 1
20 to the right until port 105 is closed.
The toroidal transmission section 20 is maintained at a desired transmission ratio. When the sleeve 102 is operated to the right as described above, the toroidal transmission section 20 is shifted to the lower speed ratio side, and the sleeve 102 is moved to the right.
When operated to the left, the gear is shifted to the high speed ratio side.

Effects of the Invention As is clear from the above explanation, according to the present invention, the trunnion rotates together with the power roller as the gear ratio changes, so the traction oil poured out from the /rJ slot of the trunnion enters the power roller. The contact parts of the output disc can be efficiently lubricated and there is no wastage of traction oil. Therefore, problems such as oil film peeling at the contact portions between the power roller and the input and output disks can be eliminated, and traction drive with good transmission efficiency can be performed at all times.

[Brief explanation of drawings]

FIG. 1 is a developed cross-sectional view of an example of a toroidal stepless fJ machine according to the present invention, FIG. 2 is a cross-sectional view taken along line nn in FIG. 1, and FIG.
The figure is a sectional view taken along the line [[[-1] of FIG. 10... Input shaft, 20... Toroidal transmission section, 21
...Input disk, 22...Output disk, 23.
24...Power roller, 25.26...Spindle, 27
．． 28... Trunnion, 27a. 27b, 27c, 28a, 28b -Q smooth hole.

Claims (1)

[Claims] (1) Input and output disks are placed opposite each other, a pair of power rollers are placed in pressure contact between the input and output disks, and the power roller is rotatably supported via a support shaft and can be moved in the axial direction. In a toroidal continuously variable transmission that is equipped with a pair of trunnions that are large and can rotate around their own axis, and that changes the gear ratio by operating the trunnions in the axial direction, a power roller is inserted inside the trunnions. A lubricating device for a toroidal continuously variable transmission, characterized in that a lubricating hole for guiding traction oil is formed in a contact portion with an output disk.