JP2931150B2 - Shift control device for hydraulically operated 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 shift control device for a hydraulically operated transmission, and more particularly, to a hydraulically operated transmission for controlling the operation of a transmission mechanism for shifting the rotation of an input member and transmitting the rotation to an output member by a hydraulic actuator. The present invention relates to a shift control device for a transmission.

[0002]

2. Description of the Related Art A transmission mounted on an automobile, particularly an automatic transmission, has a control valve for supplying and discharging hydraulic pressure to a hydraulic actuator for controlling the operation of the transmission, and a driving means for driving the control valve. Are provided.

For example, in Japanese Patent Application Laid-Open No. 63-318356, an input disk which is rotated by receiving an engine output, an output disk which is arranged coaxially with the input disk and opposed to the input disk, the output disk and the input disk A plurality of rollers disposed between and in contact with these two discs and rotating and tiltable, and a roller support member for each roller that supports each of these rollers in a rotatable and tiltable manner, A toroidal-type continuously variable transmission configured to shift the rotation of the input disk in a stepless manner and transmit the rotation to the output disk in accordance with the tilt angle by moving each roller support member in the axial direction to tilt each roller. A hydraulic actuator for tilting each roller by moving each roller support member in the axial direction, and a hydraulic actuator for the hydraulic actuator. And drive means are provided for driving the hydraulic control valve and the hydraulic control valve for controlling the hydraulic supply and discharge that.

[0004]

By the way, as can be seen in the above prior art, a hydraulic control valve constituting a toroidal type continuously variable transmission is fixed to a transmission casing side in an oil pan. The drive means for driving the valve is to be attached to the outside of the oil pan in order to prevent a function deterioration due to heat damage or the like, or to take layout characteristics into consideration. Due to the assembly error of the hydraulic control valve with respect to the transmission casing due to the constituent members or the dimensional accuracy of the transmission casing, etc., the hydraulic control valve is disposed outside the oil pan and the axis of the hydraulic control valve disposed inside the oil pan. Misalignment occurs between the shaft of the drive means and the axis of the hydraulic control valve and the shaft of the drive means are completely aligned so that both are connected Rukoto becomes difficult, smooth operation is not only impeded, cause of failure.

Accordingly, the present invention provides a shift control for a hydraulically operated transmission in which the operation of a transmission mechanism for changing the rotation of an input member and transmitting the rotation to an output member is controlled by a hydraulic actuator, as in the toroidal-type continuously variable transmission. In the apparatus, when a shift control valve for controlling supply and discharge of hydraulic pressure to the hydraulic actuator and a driving means for driving the valve are fixed to different members, the two can be surely aligned. The purpose is to do.

[0006]

Means for Solving the Problems In order to solve the above problems, the present invention is characterized in that it is configured as follows.

First, the invention according to claim 1 of the present application (hereinafter referred to as “the invention”)
A first aspect of the present invention provides a speed change mechanism that changes the speed of rotation of an input member and transmits the speed to an output member, a speed change control valve that supplies and discharges hydraulic pressure to a hydraulic actuator that controls the operation of the speed change mechanism, and the control valve. A shift control valve for a hydraulically actuated transmission, wherein the shift control valve and the drive are fixed to separate members, respectively, wherein the control is provided between the drive and the shift control valve. A positioning member having a fitting portion fitted to a valve body of the valve is provided.

The invention according to claim 2 of the present application (hereinafter referred to as “the invention”)
A second aspect of the present invention is a transmission mechanism that changes the speed of rotation of an input member and transmits the rotation to an output member, a transmission control valve that supplies and discharges hydraulic pressure to a hydraulic actuator that controls the operation of the transmission mechanism, and the control valve. And a drive unit for driving the transmission, wherein the shift control valve is disposed inside the oil pan, and the drive unit is disposed outside the oil pan. The control means has a fitting portion fitted to the valve body of the control valve, and the driving means is fixed to the wall of the oil pan via a positioning member loosely fitted to the wall of the oil pan. I do.

Further, the invention according to claim 3 of the present application (hereinafter referred to as “the invention”)
According to a third aspect of the invention, in addition to the configuration of the second aspect, a seal member is interposed between the positioning member and the drive shaft of the driving means and between the positioning member and the wall of the oil pan. It is characterized by.

Further, in the invention according to claim 4 of the present application (hereinafter referred to as a fourth invention), the positioning member according to the second invention is fitted to a valve body of a shift control valve disposed inside an oil pan. And a second fitting portion that fits into the boss of the driving means disposed outside the oil pan.

Further, the invention according to claim 5 of the present application (hereinafter referred to as the invention)
A fifth aspect of the present invention provides a gear ratio between two disks which is disposed between a pair of input / output disks opposed to each other on a rotating shaft, rotates in contact with both disks, and is tiltable. , A roller supporting member that rotatably supports the roller, and that is movable and tilts the roller according to the amount of movement, and a hydraulic actuator that moves the roller supporting member. A hydraulic control system comprising: a shift control valve for supplying and discharging hydraulic pressure; and driving means for driving the control valve, wherein the shift control valve is disposed inside the oil pan, and the drive means is disposed outside the oil pan. In the shift control device for an actuated transmission, the shift control valve includes a fitting portion fitted to a valve body of the shift control valve, and the shift control valve is provided with a positioning member loosely fitted to a wall portion of the oil pan. The drive means is fixed to the wall of the lupine, and seal members are interposed between the positioning member and the drive shaft of the drive means and between the positioning member and the wall of the oil pan. And

Further, the invention according to claim 6 of the present application (hereinafter referred to as “the invention”)
According to a sixth aspect of the present invention, the positioning member according to the fifth aspect of the present invention is configured such that the positioning member is fitted to a valve body of a shift control valve disposed inside the oil pan, and disposed outside the oil pan. A second fitting portion fitted to the boss portion of the driving means.

[0013]

According to the first aspect of the present invention, the positioning member provided between the shift control valve and the driving means has its fitting portion fitted to the valve body of the shift control valve. Will be the same. Then, in this state, the driving means is fixed to a member different from the shift control valve via the positioning means, so that the driving means and the shift control valve are fixed to separate members, respectively. Even so, by merely adjusting the mounting position of the driving means with respect to the positioning member, the axes of the driving means and the shift control valve can be completely matched, and both can be easily connected.

According to the second invention, the driving means is fixed to the wall of the oil pan through the positioning member loosely fitted to the wall of the oil pan and fitted to the valve body of the shift control valve. Therefore, even when the driving means and the shift control valve are respectively fixed inside and outside the oil pan, only by adjusting the mounting position of the driving means with respect to the positioning member, the driving means It is possible to perfectly match the axis of the transmission control valve with that of the transmission control valve and to connect the two.

Further, according to the third invention, in the second invention, between the positioning member and the drive shaft of the driving means fixed to the wall of the oil pan, and between the positioning means and the wall of the oil pan. Since a seal member is interposed between the oil pan and the oil pan,
In addition, the intrusion of the oil into the drive means is reliably prevented.

In particular, according to the fourth aspect, the positioning member has the first fitting portion fitted to the valve body of the speed ratio control valve and the second fitting portion fitted to the boss portion of the driving means. Therefore, it is possible to make the axes of the drive means and the shift control valve completely coincide with each other via the position member and easily connect the two, and thereby the drive means and the shift control valve can be easily connected. Can be more reliably performed.

According to the fifth aspect of the present invention, the transmission ratio between the two disks is increased by tilting a roller which is disposed between the pair of input / output disks, rotates in contact with the two disks, and is tiltable. In the hydraulically operated transmission configured to change the gear ratio, similarly to the second aspect of the present invention, through the positioning means fitted loosely to the wall of the oil pan and fitted to the valve body of the shift control valve. As a result, the driving means is fixed to the wall of the oil pan, so that even when the driving means and the shift control valve are respectively fixed inside and outside the oil pan, the driving means with respect to the positioning member can be fixed. By simply adjusting the mounting position, it is possible to completely align the axes of the drive means and the shift control valve and connect the two, and to drive the positioning member and the drive means. The seal member is interposed between and between the positioning means and the wall portion of the oil pan and the oil leakage into the oil pan out from the oil pan,
In addition, the intrusion of the oil into the drive means is reliably prevented.

According to a sixth aspect of the present invention, the positioning member of the fifth aspect has a first fitting portion fitted to the valve body of the speed ratio control valve and a second fitting fitted to the boss portion of the driving means. And the drive unit and the shift control valve can be completely aligned with each other through the position member to connect the two. Alignment with the shift control valve can be performed more reliably.

[0019]

Embodiments of the present invention will be described below with reference to the drawings.

FIG. 1 is an overall schematic diagram showing a power transmission system of a vehicle including a toroidal-type continuously variable transmission equipped with a shift control device according to the present invention.
A torque converter 3 connected to the output shaft 2a of the motor 2 to perform a torque increasing action, a planetary gear mechanism 10 as a reduction gear to which an output of the torque converter 3 is transmitted, and a rotation of the engine 2 which is inputted and A continuously variable toroidal type continuously variable transmission 30 having an output of the planetary gear mechanism 10 or the toroidal type continuously variable transmission 30;
Alternatively, both outputs are transmitted to the output shaft 4 so that the left and right rear wheels (not shown) are driven to rotate.

The torque converter 3 includes a pump 3b integral with a casing 3a connected to an output shaft 2a of the engine 2, and a pump 3b disposed opposite to the pump 3b.
And a stator 3d interposed between the turbine 3c and the pump 3b to perform a torque increasing operation.
and a first hollow shaft 3g fitted externally to the turbine shaft 3e and connected to the stator 3d at one end via a one-way clutch 3f to be integrated with the transmission casing 5; Are connected to the planetary gear mechanism 10. Further, the first
Externally fitted to the hollow shaft 3g and one end of the casing 3
An oil pump 6 is provided at a shaft end of the second hollow shaft 3h connected to the shaft a. The oil pump 6 is driven by the engine 2 via a casing 3a.

The planetary gear mechanism 10 has a first planetary gear mechanism 11 and a second planetary gear mechanism 12 arranged coaxially in series with the turbine shaft 3e, and a first planetary gear mechanism 12 arranged on the engine 2 side. The planetary gear mechanism 11 is used for backward movement, the second planetary gear mechanism 12 is used for forward movement, and the first planetary gear mechanism 11 is of a single pinion type and is connected to the turbine shaft 3e. A pinion 1 having a sun gear 13 and meshing with the sun gear 13
4 is rotatably supported on the carrier 15 is coupled to the first hollow shaft 3g (fixed to the transmission casing 5),
Further, a ring gear 16 meshing with the pinion 14 is connected via a reverse clutch 17 to the output shaft 4 arranged on the same axis as the turbine shaft 3e.

On the other hand, the second planetary gear mechanism 12 is of a double pinion type, and an inner pinion 18 is integrated with the pinion 14 of the first planetary gear mechanism.
The sun gear 13 of the first planetary gear mechanism 11 is shared with the sun gear of the second planetary gear mechanism 12. A carrier 20 for fixedly supporting the inner pinion 18 and the outer pinion 19 is integrated with the carrier 15 of the first planetary gear mechanism 11 and fixed to the transmission casing 5 via the first hollow shaft 3g. I have. Further, a ring gear 21 constituting the second planetary gear mechanism 12 is connected to the output shaft 4 via a forward clutch 22 and a one-way clutch 23.
The forward clutch 22 and the forward clutch 22 constitute a forward / reverse switching device. When the reverse clutch 17 is engaged, the output of the turbine shaft 3 e is transmitted to the output shaft 4 via the first planetary gear mechanism 11. Thus, the left and right rear wheels are driven to rotate in the reverse direction, and when the forward clutch 22 is engaged, the output of the turbine shaft 3 e is output via the second planetary gear mechanism 12. The power is transmitted to the output shaft 4, whereby the left and right rear wheels are driven to rotate in the forward direction.

Next, the structure of the toroidal type continuously variable transmission 30 will be described in more detail. The toroidal type continuously variable transmission 30 is disposed on the output shaft 4 as shown in FIGS. A first transmission unit 31 and a second transmission unit 32 are provided. These transmission units 31 and 32 have the same configuration, and are provided on the output shaft 4 so as to be rotatable with respect to the shaft. Input disk 3
3 and 33, and output disks 34 and 3 which are arranged to face these input disks 33 and 33 and rotate integrally with the output shaft
4 and a pair of rollers 35, 35 respectively disposed between the input / output disks 33, 34 and rotating in contact with the two disks and capable of tilting.

Then, as shown in FIG. 2, each output disk 3 in the first and second transmission units 31 and 32 is used.
The bearings 4 and 34 are spline-fitted to the output shaft 4 and the output disk 34 of the first transmission unit 31 is positioned by the ring-shaped positioning member 36 fitted to the output shaft 4. It is rotatably supported by the transmission casing 5 via 37a. Further, the output disk 34 of the second transmission unit 32 is connected to the enlarged diameter portion 4 formed integrally with the output shaft 4.
a between the output shaft 4 and the transmission casing 5.
And the input disks 33 of the first and second transmission units are disposed adjacent to each other between the output disks 34, 34, and these input disks 33 are disposed adjacent to each other. , 33, an intermediate disk 38 rotatable relative to each of the input disks 33, 33 is arranged.
A plurality of loading cams 39... 39 are interposed between the intermediate disk 38 and the input disks 33, 33, respectively.
And when the input disks 33, 33 rotate relative to each other,
Each input disk 33, 33 is connected to each output disk 34, 34.
It has a function of generating a pressing force for pressing against the input disks 33a, 33b from the engine 2, and as the input torque input to the input disks 33a, 33b from the engine 2 increases, the pressing force of the cams 39 on the input disks 33, 33 increases. It has become.

Each of the input disks 3 arranged adjacently
A connecting member 40 is loosely fitted to the output shaft 4 and spline-fitted to the input disks 33, 33 with both ends abutting against the rear surfaces of the input disks 33, 33. Are arranged, and the connecting member 40
And the input disk 33 in the second transmission unit 32
A disc spring 41 as a preload means is interposed between the input disc 33 and the disc spring 41. The disc spring 41 comes into contact with the back surface of one of the input disks 33 to press the input disk 33 toward the output disk 34. The biasing reaction force of the disc spring 41 acts on the connecting member 40, and the other input disk 33 is pressed by the connecting member 40 on the output disk 34 side.
A predetermined preload is applied to the pair of input / output disks 33, 34 in each of the transmission units 31, 32.

On the other hand, as shown in FIGS. 1 and 2, an input shaft 42 for inputting the output of the engine 2 to each input disk 33 via the intermediate disk 38 is arranged in parallel with the output shaft 4. A first gear 43 is integrally attached to an end of the input shaft 42 located on the side of the torque converter 3, and the first gear 43 is meshed with an idle gear 44. It is engaged with an output gear 46 connected to the second hollow shaft 3h via a power transmission path switching clutch 45, and is provided integrally with the intermediate disk 38 at the other end of the input shaft 42. A second gear 48 meshing with the input gear 47 provided is integrally provided. Thus, when the power transmission path switching clutch 45 is engaged, the engine 2
Output from the toroidal type continuously variable transmission 3 via the input shaft 42
1 is input to each of the input disks 33, 33 constituting the first and second transmission units 31, 32, and as shown in FIG. 1, a predetermined transmission ratio (reduction ratio) corresponding to the tilt angle of each of the rollers 35, 35 ), The rotation of each input disk 33, 33 is changed and transmitted to each output disk 34, 34.

In this embodiment, as shown in FIG. 2, the output disk 34 of the first transmission unit 31 is used.
One end of a one-way clutch 23 forming a part of the planetary gear mechanism 10 is spline-fitted. Therefore, the forward clutch 22 in the planetary gear mechanism 10 is engaged, and the reverse clutch 17 is released. When the power transmission path switching clutch 45 is engaged, the output of the engine 2 is output to the output shaft 4 via the planetary gear mechanism 10 and the toroidal type continuously variable transmission 30. In this case, the one-way clutch 23
When the rotation of the engine 2 is larger than the rear wheel side, the locked state is established. When a large torque is required such as when starting, the output of the engine 2 is increased by the torque converter 3 and the output shaft is increased. 4 will be output.

During steady running, the one-way clutch 23 is set in a free state, and the output of the engine 2 is shifted by the toroidal type continuously variable transmission 30 according to the running state and output to the output shaft 4. become.

Further, at the time of retreat, the reverse clutch 17 is engaged, the forward clutch 22 is released, and the power transmission path switching clutch 45 is released, so that the output of the engine 2 is output from the planetary gear mechanism 10.
, And is output to the output shaft 4.

Here, the toroidal type continuously variable transmission 30
A hydraulic mechanism for tilting the pair of rollers 35 in the first and second transmission units 31 and 32 will be described. The first transmission unit 3
The first side and the second transmission unit 32 have the same configuration. Therefore, the hydraulic mechanism of the first transmission unit 31 will be described, and the description of the second transmission unit will be omitted. That is, as shown in FIGS. 2 and 3, the first transmission unit 31 includes a pair of first and second trunnions 49 a, each serving as a roller supporting member for each roller 35 that rotatably supports each roller 35. 49b is provided,
These trunnions 49a, 49b have eccentric shafts 50a, 5b.
0b, each roller 35 is rotatably supported, and each trunnion 49a, 49b has a shaft member 51 extending in a direction orthogonal to the rear wheel drive shaft 4.
a and 51b are integrally attached.

Further, a pair of support members 5 are provided on the transmission casing 5 and a partition wall 5a integral with the casing 5.
2 and 53, respectively, and the first and second trunnions 49a and 4
Upper and lower ends of the shaft member 51 are rotatably supported by spherical bearings 54.
Lower ends of the lower housing 56 fixed to the lower surface of the upper housing 55 through the openings 55a of the upper housing 55 fixed to the lower surface of the partition wall 5a.
Are rotatably supported by bearings 57 in the concave portions 56a.

The partition wall 5a is provided with hydraulic cylinders 58, 58 for each of the trunnions 49a, 49b, and the hydraulic cylinders 58 are paired by a partition wall 5b integral with the partition wall 5a. Hydraulic chambers 58a, 5
8b and the partition 5b
An inner peripheral portion of the shaft member 51a, 51b integral with the first and second trunnions 49a, 49b is separated from the shaft member 51a, 51b by a predetermined gap.
Are formed. In addition, each of the hydraulic chambers 58a, 58b
The pistons 59a and 59b are respectively housed inside, and each trunnion 49 is
a, 49b, a flange 6 formed integrally with the shaft end
The flange members 61, 61 integrally attached to the shaft ends of the shaft members 51a, 51b are pressed by the other piston 59b while the flange members 61, 61 are pressed. Therefore, when hydraulic pressure is introduced into either one of the hydraulic chambers 58a and 58b, the trunnions 49a and 49b are moved by the piston 59a or the piston 59b.
b or each of the shaft members 51a and 51b is moved in the axial direction, that is, in the vertical direction in FIG.
The contact point of each roller 35 rotatably supported by 9a, 49b with each input / output disk 33, 34 changes, and each roller 35 is tilted.
9a and 49b rotate around the axis.

Next, the hydraulic chamber 5 of each of the hydraulic cylinders 58
The structure of a shift control device for controlling the supply and discharge of hydraulic oil to and from the upper and lower portions 8a and 58b will be described. As shown in FIGS. 3 and 4, a predetermined pressure from a hydraulic pressure source (not shown) is applied to the upper housing 55. The main passage 62a to which the supplied hydraulic oil is supplied, and the hydraulic chambers 58 of the hydraulic cylinders 58... 58 provided for the first and second transmission units 31 and 32, respectively.
A first passage 62b and a second passage 62c for supplying and discharging the hydraulic oil from the main passage 62a to the a and 58b are formed respectively. A transmission control device 70 is provided in the lower housing 56, and a part of the lower housing 56 serves as a valve body 72 of a hydraulic control valve 71 constituting the transmission control device 70. A sleeve 73 is inserted movably in the axial direction, and a spool 74 is inserted into the sleeve 73.

The main passage 6 is provided in the sleeve 73.
2a and the first and second ports 73b, 73b, communicated with the first and second passages 62b, 62c.
The spool 74 is provided with an annular groove 74a communicating with the main port 73a, and the first and second ports 73b and 73c are provided on the left and right sides of the groove 74a, respectively. Land portions 74b and 74c are formed.

Further, a side wall 5d 'of the oil pan 5d is provided.
Is provided with a stepping motor 75 as a rotation driving means.
A rotation member 76 is fixedly mounted on the rotation shaft 75a of the rotation member 76. A screw portion 76 integrally formed at the tip of the rotation member 76 is provided.
A drive member 77 is screwed into a. A pin member 78 is integrally fixed to the driving member 77. Both ends of the pin member 78 are connected to the valve body 72.
Are driven by a pair of upper and lower grooves 72a, 72a formed by the rotation of the stepping motor 75 to rotate the rotating member 76 and to restrict the rotation by the pin member 78 with the rotation. The member 77 is moved in the axial direction, whereby the sleeve 73 moves,
Hydraulic oil is supplied from the main port 62a to the hydraulic cylinders 58 via the first or second supply ports 62a, 62b.

A feedback means 79 is provided between the end of the spool 74 and the lower end of the shaft member 51b integral with the trunnion 49b constituting the first transmission unit 31.
The feedback means 79 is provided at the lower end of the shaft member 51b, and is provided with an inclined surface 80a which is integrally rotated with the shaft member 51b.
A first arm 82a fixed to a rotating shaft 81 rotatably provided at a predetermined position of the upper housing 55 so as to be swingable about the shaft 81 and having a leading end contacting the precess cam 80; A second arm 82b fixed to the rotating shaft 81 and capable of swinging about the shaft 81, and having a tip engaged with a slit 74b formed in the spool 74.

Further, a compression coil spring 83 as an urging means for urging the first arm 82a of the feedback means 79 toward the precess cam 80 is mounted between the driving member 77 and one end of the spool 74. .

The hydraulic control valve 71
As shown in FIGS. 3 to 5, a spacer 84 is interposed between the valve body 72 and the boss 75b of the stepping motor 75. The spacer 84 is provided on the side wall 5d of the oil pan 5d. 'Through hole 85 formed in
And the spacer 84 has a first fitting portion 8 fitted to the inner periphery of one end of the valve body 72.
4a and a second fitting portion 84b fitted to the boss portion 75b of the stepping motor 75 are formed. With the spacer 84 interposed, the flange portion 75c of the stepping motor 75 is attached to a plurality of mounting portions. Bolt 86 ... 8
6 attached to the side wall 5d 'of the oil pan 5d.

Further, oil seals 87 and 88 are mounted between the spacer 84 and the boss 75b of the stepping motor 75 and between the spacer 84 and the side wall 5d 'of the oil pan 5d, respectively.

As shown in FIG. 6, bolt insertion holes 75d... 75d formed in the flange portion 75c of the stepping motor 75 are provided with shaft portions 86a of the mounting bolts 86.
The diameter is made larger and a predetermined gap is formed between them.

According to the above configuration, the valve body 72 of the hydraulic control valve 71 and the stepping motor 75
The first fitting portion 84a of the spacer 84 provided therebetween is fitted to the valve body 72, and the axis of the spacer 84 and the valve body 72 are aligned. In this state, the boss portion 75b of the stepping motor 75 is fitted to the second fitting portion 84b of the spacer 84, and the stepping motor 75 and the side wall portion 5d 'of the oil pan 5d.
, The stepping motor 7
5 and the hydraulic control valve 71 are fixed to the inside and outside of the oil pan 5d, and even if there is a displacement due to an assembly error or the like between the two mounting positions, the axes of the two are completely aligned. The two can be easily connected.

Further, the spacer 84 and the oil pan 5d
Oil seals 87, 88 between the spacer 84 and the side wall 5d 'of the oil pan 5d between the rotating shaft 75a of the stepping motor 75 fixed to the side wall 5d' of the oil pan 5d.
Is provided, it is possible to reliably prevent oil from leaking from the inside of the oil pan 5d to the outside of the oil pan 5d and the oil from entering the stepping motor 75 side.

Although the present embodiment has been described with reference to the case where the transmission control device of the hydraulically operated transmission according to the present invention is provided in the toroidal type continuously variable transmission 30, the hydraulically operated transmission according to the present invention is not limited to this. The transmission to which the transmission control device is applied is not limited to the toroidal-type continuously variable transmission 30, and it goes without saying that the transmission can be applied to various devices.

[0045]

As described above, according to the first aspect of the present invention, when the positioning member is aligned with the axis of the transmission control valve, the driving means is connected to the transmission control valve via the positioning member. Is fixed to a separate member, even if the drive means and the shift control valve are fixed to separate members and there is a displacement due to an assembly error or the like at each mounting position, By merely adjusting the mounting position of the driving means with respect to the positioning member, the axes of the driving means and the shift control valve can be completely matched, and the two can be easily connected.

According to the second aspect of the present invention, even when the drive means and the shift control valve are respectively fixed inside and outside the oil pan, the drive means with respect to the positioning member is provided in the same manner as in the first invention. By simply adjusting the mounting position, the axis of the drive means and the axis of the shift control valve can be completely matched, and both can be easily connected.

Further, according to the third invention, the positioning member is interposed between the driving shaft of the driving means fixed to the wall of the oil pan and the positioning means and the wall of the oil pan. The seal member can reliably prevent oil from leaking from the inside of the oil pan to the outside of the oil pan and intrusion of the oil into the drive means side.

In particular, according to the fourth aspect, the positioning member has the first fitting portion fitted to the valve body of the speed ratio control valve and the second fitting portion fitted to the boss portion of the drive means. Therefore, it is possible to completely align the axis of the drive means and the shift control valve via the position member and to connect the two, and thereby, the drive means and the shift control valve can be connected to each other. Alignment can be performed more reliably.

According to the fifth aspect of the present invention, the gear ratio between the two disks is increased by tilting the roller which is disposed between the pair of input / output disks, rotates in contact with the disks, and is tiltable. In the case of a hydraulically operated transmission configured to change the speed, the driving means and the shift control valve are respectively fixed inside and outside the oil pan, and there is a shift due to an assembly error or the like at each mounting position. Even in the case of the second aspect of the invention, just by adjusting the mounting position of the driving means with respect to the positioning member, the axes of the driving means and the shift control valve are completely matched and the two are easily connected. And a sealing member interposed between the positioning member and the drive shaft of the driving means and between the positioning means and the wall of the oil pan. Oil leakage to the outside Lupine, and entering the drive means side of the oil is to be reliably prevented.

According to the sixth aspect of the present invention, the positioning member of the fifth aspect has a first fitting portion fitted to the valve body of the speed ratio control valve and a second fitting portion fitted to the boss of the drive means. And the drive unit and the shift control valve can be completely aligned with each other through the position member to connect the two. Alignment with the shift control valve can be performed more reliably.

[Brief description of the drawings]

FIG. 1 is an overall schematic configuration diagram showing a power transmission system of a vehicle including a toroidal-type continuously variable transmission including a transmission control device according to the present invention.

FIG. 2 is an enlarged sectional view showing a configuration of a toroidal type continuously variable transmission.

FIG. 3 is a cross-sectional view of a first transmission unit included in the toroidal-type continuously variable transmission, taken along line AA in FIG. 2;

FIG. 4 is an enlarged sectional view of a transmission control device.

FIG. 5 is an enlarged sectional view of a main part of the transmission control device.

FIG. 6 is a partially enlarged plan view showing a mounting state of the stepping motor.

[Description of Signs] 4 Output shaft 5d Oil pan 5d 'Side wall 30 Toroidal-type continuously variable transmission 33 Input disk 34 Output disk 35 Rollers 49a, 49b Trunnion 58 Hydraulic cylinder 70 Transmission control device 71 Hydraulic control valve 72 Valve body 75 Stepping Motor 84 Spacer 84a First fitting portion 84b Second fitting portion 87,88 Oil seal

Continuation of the front page (56) References JP-A-63-318356 (JP, A) JP-A-2-85560 (JP, A) JP-A-3-89066 (JP, A) JP-A-6-121459 (JP) , U) (58) Fields investigated (Int. Cl. ⁶ , DB name) F16H 61/00 F16H 15/38

Claims (6)

(57) [Claims] A speed change mechanism for changing the speed of rotation of an input member and transmitting the speed to an output member; a speed change control valve for supplying and discharging hydraulic pressure to a hydraulic actuator for controlling the operation of the speed change mechanism; A shift control valve for a hydraulically operated transmission, wherein the shift control valve and the drive means are fixed to separate members, respectively, wherein the control is provided between the drive means and the shift control valve. A shift control device for a hydraulically operated transmission, comprising a positioning member having a fitting portion fitted to a valve body of the valve. 2. A speed change mechanism for shifting the speed of rotation of an input member and transmitting the speed to an output member, a speed change control valve for supplying and discharging hydraulic pressure to a hydraulic actuator for controlling the operation of the speed change mechanism, and driving the control valve A shift unit for a hydraulically operated transmission, wherein the shift control valve is disposed inside an oil pan, and the drive unit is disposed outside the oil pan. The drive means has a fitting portion fitted to the valve body of the control valve, and the driving means is fixed to the wall of the oil pan via a positioning member loosely fitted to the wall of the oil pan. A shift control device for a hydraulically operated transmission. 3. A speed change mechanism for changing the speed of rotation of an input member and transmitting the speed to an output member, a speed change control valve for supplying and discharging hydraulic pressure to a hydraulic actuator for controlling the operation of the speed change mechanism, and driving the control valve. A shift unit for a hydraulically operated transmission, wherein the shift control valve is disposed inside an oil pan, and the drive unit is disposed outside the oil pan. The drive means has a fitting portion fitted to the valve body of the control valve, and the driving means is fixed to the wall portion of the oil pan via a positioning member loosely fitted to the wall portion of the oil pan, A shift control device for a hydraulically operated transmission, wherein a seal member is interposed between the positioning member and a drive shaft of the driving means and between the positioning member and a wall of the oil pan. . 4. A speed change mechanism for changing the speed of rotation of an input member and transmitting the speed to an output member, a speed change control valve for supplying and discharging hydraulic pressure to a hydraulic actuator for controlling the operation of the speed change mechanism, and driving the control valve. A shift unit for a hydraulically operated transmission, wherein the shift control valve is disposed inside an oil pan, and the drive unit is disposed outside the oil pan. A positioning member having a first fitting portion fitted to the valve body of the control valve and a second fitting portion fitted to the boss portion of the driving means, and being loosely fitted to the wall of the oil pan; A shift control device for a hydraulically operated transmission, wherein the drive unit is fixed to a wall of the oil pan via a wall. 5. A speed change ratio between the two disks, which is disposed between a pair of input / output disks opposed to each other on a rotating shaft, rotates in contact with the two disks, and is tiltable, and changes the speed ratio between the two disks according to the tilt angle. A roller that rotatably supports the roller, and a roller support member that is movable and tilts the roller according to the amount of movement, and a hydraulic actuator that moves the roller support member. A hydraulically operated type having a shift control valve for supplying and discharging, and a driving means for driving the control valve, wherein the shift control valve is disposed inside the oil pan and the driving means is disposed outside the oil pan A shift control device for a transmission, comprising: a fitting portion fitted to a valve body of the shift control valve; and a positioning member loosely fitted to a wall portion of the oil pan. The drive unit is fixed to the wall of the oil pan, and a seal member is interposed between the positioning member and the drive shaft of the drive unit and between the positioning member and the wall of the oil pan. A shift control device for a hydraulically operated transmission, comprising: 6. A speed change ratio between two disks is arranged between a pair of input / output disks opposed to each other on a rotating shaft, is rotated in contact with the two disks, and is tiltable, and changes according to the tilt angle. A roller that rotatably supports the roller, and a roller support member that is movable and tilts the roller according to the amount of movement, and a hydraulic actuator that moves the roller support member. A hydraulically operated type having a shift control valve for supplying and discharging, and a driving means for driving the control valve, wherein the shift control valve is disposed inside the oil pan and the driving means is disposed outside the oil pan A shift control device for a transmission, comprising: a first fitting portion fitted to a valve body of the shift control valve; and a second fitting portion fitted to a boss portion of the driving means,
A shift control device for a hydraulically operated transmission, wherein the driving means is fixed to a wall of the oil pan via a positioning member loosely fitted to a wall of the oil pan.