JP3193967B2 - 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 transmits a rotation of an input disk to an output disk via a power roller sandwiched between an input disk and an output disk, and continuously adjusts the ratio of the rotation speeds of both disks. The present invention relates to a toroidal-type continuously variable transmission that can be changed to a constant.

[0002]

2. Description of the Related Art A continuously variable transmission capable of transmitting the rotation of an input disk to an output disk while changing the number of rotations and continuously changing the ratio of the number of rotations (speed ratio) is a toroidal type continuously variable transmission. Transmission (hereinafter, T-CVT)
Also abbreviated) has been developed. This T-CVT has a structure in which an input disk and an output disk having a substantially conical shape are opposed to each other, and a plurality of power rollers are arranged in a toroidal space formed therebetween. And
The input disk is rotated by an external rotational driving force input from the input shaft, and the output disk is rotated in the opposite direction by the power roller being pinched between the input and output disks. In this way, the rotation is transmitted from the input disk to the output disk, and by changing the inclination of the power roller, the distance from each contact point between the power roller and the input / output disk to the center of the shaft is changed to change the gear ratio. Change continuously.

As one type of such a T-CVT, a T-CVT in which an input shaft is arranged coaxially with a rotation center of an input / output disk.
A VT has been developed and is disclosed, for example, in Japanese Utility Model Laid-Open Publication No. 2-47458. In the T-CVT, an input disk and an output disk are rotatably supported on an input shaft. The T-CVT of the type in which the input and output shafts are provided coaxially can reduce the size and weight and the number of parts as compared with the T-CVT in which the input shaft and the output shaft are provided separately. The advantage is that production costs can be reduced because of the reduction.

[0004]

However, in this type of T-CVT, the output disk is supported on the input shaft via an output disk bearing. Since the output disk rotates in the reverse direction with respect to the input shaft, the output disk bearing receives the rotational speed obtained by adding the rotational speed of the output disk to the rotational speed of the input shaft, and is consumed in a short period of time. On the other hand, the input disk is also supported on the input shaft via an input disk bearing, but is pressed by an input cam flange which rotates integrally with the input shaft and rotates at the same rotational speed as the input shaft. Therefore, the input disk bearing does not need to receive the difference in the number of rotations of the input shaft and the input disk, and wear is extremely reduced. As described above, not only the bearing for the output disk is worn out in a short period of time, but also the running speed of the two bearings is remarkably different due to the remarkably different wear speed. Had increased costs. Therefore, an object of the present invention is to provide a toroidal-type continuously variable transmission that can suppress wear of bearings and average wear of each bearing.

[0005]

In order to solve the above-mentioned problems, the present invention is configured as follows. That is,
An input disk that rotates by receiving torque,
An output disk facing the input disk; and a power roller sandwiched between the output disk and the input disk. The rotation speed of the input disk and the output disk is changed by changing the inclination of the power roller. The toroidal type continuously variable transmission has a housing, and a fixed shaft is fixed to the housing. The input disk is rotatably supported on the fixed shaft via a first bearing, and the output disk is rotatably supported on the fixed shaft via a second bearing. The power roller is provided between the input disk and the output disk, and can change a rotation ratio of the input disk and the output disk by changing a tilt. Third bearing for receiving an axial reaction force acting on the input disk and the output disk
And the fourth bearing, and of these axial reaction forces
Transfer the difference from the third or fourth bearing through the fixed shaft.
It is configured to be received by the housing .

[0006]

In the toroidal type continuously variable transmission according to the present invention,
An input disk is rotatably supported via a first bearing on a shaft of a fixed shaft which is fixed to a housing of the toroidal type continuously variable transmission and does not rotate, and an output disk is rotatably supported via a second bearing. I have. That is, since the fixed shaft is not a shaft for transmitting torque, the second bearing supporting the output disk with respect to this fixed shaft receives only the rotation speed of the output disk, and the speed of wear is significantly reduced. You. Similarly, the first bearing supporting the input disk with respect to the fixed shaft also receives only the rotation speed of the input disk, so that the speed of wear is approximately equal to that of the second bearing. Further, the axial reaction force acting on the input disk and the output disk is received by the third bearing and the fourth bearing, and the difference between these axial reaction forces is reduced by the third bearing or the third bearing.
In the housing from the fourth bearing through the fixed shaft
I can take it. Therefore, the transmission of the rotational force between the input disk and the output disk by the power roller is performed efficiently. As a result, the wear of each bearing described above is suppressed, and the wear of each bearing is averaged, so that the timing for replacing each bearing can be made uniform, thereby reducing running costs.

[0007]

Next, an embodiment of the present invention will be described with reference to FIGS. FIG. 1 is a longitudinal sectional view showing one embodiment of a toroidal type continuously variable transmission according to the present invention. In this embodiment, a toroidal type continuously variable transmission according to the present invention is provided with a mechanical supercharger (supercharger,
This is an example in which the present invention is applied as a transmission device (hereinafter also abbreviated as SC). In FIG. 1, a toroidal type continuously variable transmission (T
-CVT) 1 and a roots-type mechanical supercharger (SC) 100 in the right half. This T-CVT
1 includes an input disk 30 and an output disk 24 that rotate around the fixed shaft 18 and two power rollers 158 provided in the space between the two disks 30 and 24 with the fixed shaft 18 interposed therebetween. Have been.

The fixed shaft 18 is integrally formed with a retainer 2 at one end (the right end in the figure), and the retainer 2 is fixed to the SC case 10. The SC case 10 is fixed to the CVT case 82 via the intermediate case 14, and these cases 10, 14,
82 together constitute a housing of the T-CVT 1. Therefore, the fixed shaft 18 is fixed to the housings 10, 14, 82 of the toroidal type continuously variable transmission 1. On the other hand, a nut 54 is screwed to the other end (left end in the figure) of the fixed shaft 18, and the outer periphery of the nut 54 is connected to the pulley 7 via an angular type ball bearing 52.
0 is rotatably mounted. The pulley 70 is supported by a front case 74 by a ball bearing 64 and by a CVT case 82 by a needle bearing 44. Note that an oil seal 62 is attached to seal oil from the ball bearing 64 to the outside.

An oil pump 50 is formed on the mating surface between the front case 74 and the CVT case 82. The oil pump 50 is for supplying lubricating oil to each part of the T-CVT 1, and the front case 74 also serves as a case of the oil pump 50. Oil pump 5
0 is driven by the rotation of the pulley 70, and pumps oil from the suction port 180 to the discharge port 182. The power transmitted to the pulley 70 is transmitted to the cam race 34 by the spline 46. The torque cam 32 provided on the cam race 34 generates an axial force in the right direction in the figure according to the magnitude of the torque input from the cam race 34. The output race of the torque cam 32 is formed on the back of the input disk 30. The cam race 34
It is rotatably supported on the fixed shaft 18 via a needle bearing 40. The input disk 30 is rotatably supported on the fixed shaft 18 via a needle bearing 28. That is, this needle bearing 2
Reference numeral 8 functions as a first bearing that rotatably supports the input disk 30 on the fixed shaft 18.

A spacer 38 is interposed between the cam race 34 and the pulley 70, and a disc spring 36 is interposed between the spacer 38 and the cam race 34. The disc spring 36 is for applying an initial axial force to the cam race 34. Therefore, by tightening the nut 54, the initial axial force by the disc spring 36 is adjusted. The front side of the ball bearing 52 is covered with a front cover 58.

The input disk 30 on the fixed shaft 18
An output disk 24 is rotatably supported at a position facing the output disk 24 via a needle bearing 26. That is, the needle bearing 26 functions as a second bearing that rotatably supports the output disk 24 on the fixed shaft 18. Input disk 30 and output disk 24
In the toroidal cavity formed between
Two power rollers 158 are provided and constitute a main part of the continuously variable transmission function of the T-CVT1. T of this embodiment
The operation principle of the CVT 1 is not special, and is the same as that of the toroidal type continuously variable transmission disclosed in, for example, Japanese Patent Application Laid-Open No. 58-160664.

A primary shaft 8 rotatably fitted to the outer periphery of the fixed shaft 18 is connected to the output disk 24 by a spline 22. The primary shaft 8 is also rotated around the fixed shaft 18 at the rotation speed of the output disk 24. You. The primary shaft 8 is rotatably supported on the intermediate case 14 and the SC case 10 by ball bearings 16 and angular ball bearings 4 at both ends. A drive gear 20 is press-fitted between the output disk 24 and the ball bearing 16 at the left end of the primary shaft 8 in the drawing. The rotation of the primary shaft 8 is performed via the drive gear 20 via the drive gear 2.
0 is transmitted to the driven gear 80 meshing with the upper part of the figure.

The driven gear 80 is a secondary shaft 9
The secondary shaft 92 is rotatably supported by the intermediate case 14 and the SC case 10 at both ends by angular ball bearings 88 and 96 at both ends. Since the drive gear 20 and the driven gear 80 have the same number of teeth (that is, the gear ratio is 1: 1), the primary shaft 8 and the secondary shaft 92 rotate in reverse at the same rotation speed. An initial axial force is applied to the ball bearing 88 and the ball bearing 96 by a disc spring 86, and the disc spring 86 is pressed by a snap ring 84. The eyebrows-type rotors 6 and 94 are attached to the primary shaft 8 and the secondary shaft 92, respectively, to constitute a roots-type SC100. In addition, the ball bearing 4 on the rear side of the roots type SC100
And the ball bearing 96 are pressed by fixing retainers 2 and 98, respectively. The fixed shaft 18 described above is integrated with the retainer 2 on the primary side.

With the above structure, the rotational driving force of the engine crankshaft (not shown) is transmitted to the pulley 70 via a belt (not shown), and the rotation of the pulley 70 is transmitted to the input disk 30 via the torque cam 32. Further, the rotation of the input disk 30 is transmitted to the output disk 24 by the power roller 158, and the output disk 24 rotates reversely. Thereby, the primary shaft 8 and the secondary shaft 92 rotate, respectively, and the roots-type SC 100 is driven. At this time, when the reaction force pressing the input disk 30 in the front direction (left direction in FIG. 1) is large among the axial reaction forces generated in the T-CVT 1 ,
The reaction force is generated by the cam race 34, the spacer 38, the pulley 7
0, ball bearing 52 (third bearing) , nut 5
4, SC case 10 via fixed shaft 18 and retainer 2
(A component part of the housing). On the other hand, the reaction force pushing the output disk 24 rearward (to the right in FIG. 1) is large.
When stiff, the reaction force is determined by the drive gear 20, primary shaft 8, ball bearing 4 (fourth bearing) , and fixed
It is also received in the SC case 10 via the shaft 18 and the retainer 2. Also, assume that the speed ratio of T-CVT1 is "1".
Act on the input disk 30 and the output disk 24
Axial reaction forces are equal to each other. Therefore input disk
The axial reaction force acting on the ball 30 is applied to the ball from the retainer 2.
Enters and exits the primary shaft 8 through the bearing 4
The axial reaction force acting on the force disk 24 is
Enter the primary shaft 8 from a. As a result,
Axial reaction forces are offset by the primary shaft 8
To zero.

Next, the structure of the power roller 158 will be described with reference to FIG. FIG. 4 is a longitudinal sectional view showing a support structure of the power roller 158 and a structure for changing the inclination thereof, and corresponds to a cross-sectional view taken along the line IV-IV in FIG. The pair of power rollers 158 are rotatably supported on the trunnion 168 via needle bearings 166, shafts 164, needle bearings 162, and ball bearings 160. The trunnion 168 is supported on the upper side by the bearing 156 on the upper link 152 and on the lower side by the bearing 170 on the lower link 120. A pair of trunnions 168 and upper and lower links 1
52 and 120 form a cross-girder structure. Further, the upper link 152 is formed by the upper post 148.
Lower link 120 is CVT by lower post 122.
It is supported by the case 82. A bolt 132 forming a ball screw 138 is press-fitted into the upper end of each trunnion 168, and the ball screw 138 is supported on the CVT case 82 by a ball bearing 134 via a female nut 140. The ball bearing 134 is held down by a retainer 136.

The female nut 140 is connected to the pivot shaft 151.
, The angle of the trunnion 168 and the power roller 158 around the pivot shaft 151 is changed. As a result, the position of the contact point between the power roller 158 and the input disk 30 and the output disk 24 shown in FIG.
The gear ratio of T1 is determined. The upper portion of the power roller driving portion is protected by an upper cover 144. The female nut 140 is connected to the arm 116 via a pin 142.
6 is connected to the rod 112. The arm 116 is
It is attached to a nut 140 via a pin 142.
As shown in the partial cross-sectional view of FIG. 2, a hydraulic piston 106 is formed at the tip of the rod 112, and the hydraulic piston 106
Can be slid left and right. When oil flows into the hydraulic chamber 104 formed on the left side of the hydraulic piston 106 in the figure, the hydraulic piston 106 is moved rearward (rightward in the figure).
And the speed ratio of T-CVT1 changes to the speed increasing side. On the other hand, when oil flows out of the hydraulic chamber 104, the hydraulic piston 106 moves in the front direction (left direction in the drawing) by the urging force of the spring 108 inserted between the hydraulic cylinder 110 and the hydraulic piston 106, and the T-CVT1 Is changed to the deceleration side.

As a hydraulic control system for taking oil in and out of the hydraulic chamber 104, hydraulic control valves are built in a front portion 102 of the CVT case 82 shown in FIGS. As shown in FIG. 1, the oil pump 50 is provided on the mating surface of the front part 102 and the front case 74, and a control system oil passage described below.
Further, the hydraulic chamber 104 is constituted. Further, FIG.
As shown below, since the outlet 178 of the strainer 23 in the oil pan 118 is also formed in the front part 102, all of the hydraulic system is concentrated on the front part 102 of the CVT case 82.

Next, the configuration of the hydraulic system will be described mainly with reference to FIG. FIG. 3 is a longitudinal sectional view showing the hydraulic system of the T-CVT 1, and corresponds to a sectional view taken along the line III-III in FIG. The oil from the strainer 23 in the oil pan 118 shown in FIG. 1 is supplied to the oil holes 178 and 17 shown in FIG.
6, and is sucked into the oil pump 50 (see FIG. 1) through the suction port 180. Then, the oil discharged from the discharge port 182 is supplied to the primary regulator valve 190 and the flow valve 192 via the oil passage 172. This primary regulator valve 190
The pressure of the hydraulic line is set by the
Thus, whether the oil flows into the hydraulic chamber 104, the oil flows out from the hydraulic chamber 104, or the hydraulic chamber 104 is closed is controlled. The control pressure oil passage 191 is connected between the primary regulator valve 190 and the flow valve 192.

Further, an electric pulse signal having a duty ratio is converted into a hydraulic signal called a control pressure by a duty valve 114 provided behind the control pressure oil passage 191, which controls a flow valve 192. FIG. 5 illustrates this. An electric pulse signal corresponding to the duty ratio is supplied to the duty valve 114 by an electric circuit (not shown). Then, as shown in FIG. 5, the control pressure increases in proportion to the magnitude of the duty ratio. When the control pressure is from zero to a certain level, the duty valve 1
Numeral 14 allows oil to flow out of the hydraulic chamber 104, and closes the hydraulic chamber 104 when the control pressure reaches a certain level. When the control pressure further increases, the hydraulic chamber 104
The oil is allowed to flow in.

The oil relieved from the primary regulator valve 190 is supplied to the secondary regulator valve 1
88 determines the lubrication pressure. With this lubricating pressure, lubricating oil is supplied to each part of the T-CVT 1 via the lubricating oil passage 186. As shown in FIG. 1, the lubricating oil is first passed to the upper post 148 through the oil hole 72, and is further input to the input disk 3 through the oil holes 146, 150 and 78.
0 and the output disk 24. Next, the oil in the oil hole 150 is supplied to the oil passage inside the fixed shaft 18 through the pipe 154, and the bearing 2 is inserted through the oil holes 48 and 66.
6, 28, 40, 52, splines 22, 46, torque cam 32 and the like are lubricated. The illustrated left end of the oil hole 48 formed in the fixed shaft 18 is sealed by a cap 56. The oil seals 12 and 90 are provided on the right side of the ball bearing 16 and the ball bearing 88 in the drawing. The oil lubricating the ball bearing 52 is discharged from the oil hole 60.

Further, as shown in FIG. 3, the oil from the lubricating oil passage 186 is filled with oil holes 17 provided at two places on the left and right.
4 through the left and right side posts 124 shown in FIG.
Passed to Further, the lubrication of the bearing 160 of the power roller 158 to the trunnion 168 through the oil holes 126, 128, and 130 is performed. Oil pump 5
The capacity of 0 is an amount necessary for the above-described lubrication, and also ensures an inflow amount into the hydraulic chamber 104. The oil finally used for lubrication, the oil relieved from the secondary regulator valve 188, and the oil flowing out of the flow valve 192 return to the oil pan 118 shown in FIG. 1 or FIG. Note that, as shown in FIG. 1, the hydraulic system of the T-CVT 1 includes the front case 74 and the front part 10 of the CVT case 82.
2 and is sealed by a packing 184 provided therebetween.

In the toroidal-type continuously variable transmission (T-CVT) 1 having the above-described configuration, the rotation of the pulley 70 is transmitted to the input disk 30 via the torque cam 32, and further the output disk 2 is transmitted by the power roller 158.
4, the output disk 24 rotates in the reverse direction. As a result, the primary shaft 8 and the secondary shaft 92 rotate, and the roots-type SC 100 is driven at a speed ratio defined by the inclination of the power roller 158. Here, the input disk 30 and the output disk 2
Reference numeral 4 denotes a first bearing 28 and a second bearing 26 around a fixed shaft 18 fixed to the SC case 10, the intermediate case 14, and the CVT case 82 constituting the housing of the T-CVT 1.
It is rotatably supported through. Therefore, the second bearing 26 receives only the rotation speed of the output disk 24, and the speed of wear is significantly reduced. On the other hand, the first bearing 28 also receives the number of rotations of the input disk 30, so that the speed of wear is approximately equal to that of the second bearing 26. Further, the third roller 52 and the fourth bearing 4 allow the power roller 1
The axial reaction force received by the input disk 30 and the output disk 24 can be received via the input disk 58, and the transmission of the rotational force by the power roller 158 can be performed efficiently.
In this way, the wear of the bearings can be suppressed and the wear of each bearing can be averaged.

In the present embodiment, needle bearings 28 and 26 are used as the first and second bearings,
Ball bearings 52 as bearings and fourth bearings,
4, but other types of bearings can be used for any part. The shape, size, number, material, arrangement, and the like of other parts of the toroidal-type continuously variable transmission are not limited to the present embodiment. Further, as an effect peculiar to the present embodiment, since the pulley 70 is supported on the nut 54 screwed to the fixed shaft 18 via the ball bearing 52, the shaft corresponding to the fixed shaft even in the same T-CVT is used. There is an advantage that the wear of the ball bearing 52 is significantly reduced as compared with the type in which the pulley 70 rotates in the reverse direction.

[0024]

According to the present invention, a first bearing and a second bearing rotatably supporting an input / output disk on a fixed shaft fixed to a housing of a toroidal type continuously variable transmission, and an axial direction of the input / output disk. Since the toroidal-type continuously variable transmission having the third bearing and the fourth bearing that are responsible for the reaction force is created, the wear of each bearing can be suppressed and averaged. As a result, the durability of the bearings is increased, and the bearings can be replaced at the same time, so that the working efficiency is improved. Therefore, the running cost can be remarkably reduced, and an extremely practical toroidal type continuously variable transmission can be obtained.

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional view showing an embodiment of a toroidal type continuously variable transmission according to the present invention.

FIG. 2 is a partial cross-sectional view showing a part of the toroidal-type continuously variable transmission, and corresponds to a cross-sectional view taken along a line II-II in FIG.

FIG. 3 is a longitudinal sectional view showing a hydraulic system of the T-CVT, and corresponds to a sectional view taken along line III-III of FIG.

FIG. 4 is a longitudinal sectional view showing a support structure of the power roller of the T-CVT and a structure for changing the inclination thereof, and FIG.
It corresponds to the IV section view.

FIG. 5 is an explanatory diagram showing an operation of a hydraulic system of the T-CVT1.

[Explanation of symbols]

 Reference Signs List 1 toroidal-type continuously variable transmission 4 fourth bearing 10, 14, 82 housing 18 fixed shaft 24 output disk 26 second bearing 28 first bearing 30 input disk 52 third bearing 158 power roller

──────────────────────────────────────────────────続 き Continuation of front page (56) References JP-A-2-300549 (JP, A) JP-A-58-160664 (JP, A) JP-A-2-47458 (JP, U) (58) Survey Field (Int.Cl. ⁷ , DB name) F16H 15/38

Claims (1)

(57) [Claims] An input disk rotating by receiving a torque, an output disk facing the input disk, and a power roller sandwiched between the output disk and the input disk; A toroidal-type continuously variable transmission that changes the ratio of the number of revolutions of the input disk to the output disk by changing the inclination of the input disk and the output disk. The toroidal-type continuously variable transmission has a housing, and a fixed shaft is fixed to the housing. Wherein the input disk is rotatably supported on the fixed shaft via a first bearing; the output disk is rotatably supported on the fixed shaft via a second bearing; and the power roller is the input disk. Is provided between the input disk and the output disk to change a rotation ratio of the input disk and the output disk. Bets can be, axial direction that acts on said input disk and said output disk
The third and fourth bearings receive the reaction force.
And the difference between these axial reaction forces is
A fourth bearing is received by the housing through the fixed shaft.
A toroidal-type continuously variable transmission characterized in that it is configured to be driven.