JPH07332451A - Change gear ratio control device for toroidal type vontinuously variable transmission - Google Patents

Abstract

PURPOSE:To perform execution of control of a change gear ratio to a proper value without increasing capacity of a gear shift motor to a more than necessary value by providing a gear shift motor to drive the valve member of a gear shift control valve and a mechanical reduction gear to transmit the drive force of the gear shift motor after reduction thereof. CONSTITUTION:During a gear shift, a stepping motor 70 is rotationally driven to an angle corresponding to a target inclination angle (a target change gear ratio) according to a signal outputted from a control unit. This rotational drive force is transmitted to a collar through a mechanical reduction gear 68 and through the screw feed of the collar, a sleeve 65 is axially moved. As a result, the main port of the sleeve 65 is communicated with the first or second port of a valve body 64 through a group of spools 66. This constitution feeds an oil pressure to given oil pressure chambers 56 and 57 and displaces a power roller 35 to a target inclination angle.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a gear ratio control device for a toroidal type continuously variable transmission in which a power roller is installed between an input disk and an output disk.

[0002]

2. Description of the Related Art Conventionally, for example, JP-A-63-225755.
As disclosed in Japanese Patent Laid-Open Publication No. 2004-242242, a pair of power rollers are arranged between an input disk to which driving torque is input from an automobile engine and an output disk for outputting driving torque to the driving wheels. A gear ratio control device for a toroidal type continuously variable transmission configured to adjust a gear ratio by displacing a supporting member that rotatably supports a shaft in an axial direction thereof to change a tilt angle of a power roller. Are known.

In the above gear ratio control device, a gear ratio control valve having a three-layer structure in which a sleeve and a spool are arranged in a valve body, and a male screw portion which is screwed to a female screw portion formed on the sleeve are formed. And a variable speed motor including a stepping motor that rotationally drives the drive rod. Then, the gear ratio control is executed by rotationally driving the drive rod by the speed change motor and screwing the sleeve.

[0004]

SUMMARY OF THE INVENTION As described above, in the structure in which the valve member including the sleeve of the shift control valve is screwed by the driving force of the shift motor, as described above, the sleeve and the drive for screwing the same. If the shaft center of the transmission is not exactly aligned with that of the rod, the drive resistance when the sleeve is screwed will increase significantly, and if this drive resistance becomes larger than the drive force of the transmission motor, the step-out of the transmission motor will be lost. There is a problem that a phenomenon may occur and the state may fall out of control.

In the above conventional device, a relatively large gap is provided in the connecting portion between the drive shaft of the transmission motor and the drive rod, so that the concentricity of the shaft center of the transmission motor and the transmission control valve absorbs an error. However, even in this configuration, if there is an error in the degree of concentricity between the sleeve and the axis of the drive rod, the threaded portion of the sleeve and the drive rod may be fixed. This is unavoidable, and there is a problem that a step-out phenomenon occurs in the above-mentioned transmission motor.

Further, as shown in FIG. 8, the valve body 6
In a three-layer structure shift control valve having a sleeve 4, a sleeve 65 and a spool 66, a spring 67 forming a control actuator and a stepping motor 70 are arranged at one end of the spool 66. The rotating member 94 connected to the output shaft of 70 has a collar 95.
It is known that the collar 95 and the sleeve 65 are engaged with each other via a pin member 96 while being screwed.
Then, the rotation member 94 is rotationally driven by the stepping motor 70 to screw the collar 95, and the sleeve 65 is slidably displaced in the axial direction thereof against the biasing force of the spring 67, whereby the shift control is performed. Is being done.

The gear ratio control valve having the above-described structure is capable of screwing the collar 95 without trouble even when the output shaft of the stepping motor 70 and the sleeve 65 are not exactly aligned with each other. While having advantages,
If the installation angle of the pin member 96 that connects the collar 95 and the sleeve 65 is not accurately set, the collar 95 is
An eccentric load acts on the collar 95 and the rotating member 9
The screwed portion with 4 will be fixed. In order to prevent such a situation from occurring, the stepping motor 70
Since it is necessary to sufficiently increase the capacity of the variable speed motor consisting of, the layout is difficult and the weight is increased.

The present invention has been made to solve the above problems, and is a toroidal type continuously variable transmission capable of properly executing the gear ratio control without increasing the capacity of the transmission motor more than necessary. An object of the present invention is to provide a gear ratio control device for a machine.

[0009]

The invention according to claim 1 is
A power roller installed between the input disc and the output disc, a support member that rotatably supports the power roller, a hydraulic mechanism that displaces the support member in the axial direction thereof, and a control hydraulic pressure to the hydraulic mechanism. A toroidal type continuously variable transmission having a gear ratio control valve to be supplied, and a gear reducer for driving a valve member of the gear change control valve, and a gear reducer for reducing the driving force of the gear change motor and transmitting the speed to the valve member. And are provided.

According to a second aspect of the present invention, in the gear ratio control device for a toroidal type continuously variable transmission according to the first aspect, a gear shift motor for driving a valve member of the gear ratio control valve is installed in the gear ratio control valve. It is arranged at a position offset above.

According to a third aspect of the present invention, in the gear ratio control device for a toroidal type continuously variable transmission according to the second aspect, the shaft center of the gear ratio control valve is arranged in the lower portion of the valve body.

According to a fourth aspect of the present invention, a power roller installed between the input disk and the output disk, a support member for rotatably supporting the power roller, and the support member displacing in the axial direction thereof. In a toroidal type continuously variable transmission having a hydraulic mechanism and a gear ratio control valve that supplies control hydraulic pressure to the hydraulic mechanism, a driven portion of a valve member is located outside an gear ratio control valve, and A biasing member for biasing the member toward the driven portion thereof, and a pushing member for pushing the driven portion toward the inner side of the gear ratio control valve against the biasing force of the biasing member, A shift motor for driving the pushing member is provided.

[0013]

According to the invention described in claim 1, the driving force of the gear ratio control valve is reduced by the gear reducer and transmitted to the valve member of the gear ratio control valve, and the valve member is driven with a large driving force. As a result, the gear ratio control of the toroidal type continuously variable transmission is properly executed.

According to the second aspect of the present invention, it is possible to secure an installation space for the transmission motor and the gear reducer for driving the transmission ratio control valve without increasing the size of the transmission.

According to the third aspect of the invention, since the gear ratio control valve is installed at a position apart from the hydraulic mechanism of the toroidal type continuously variable transmission, the reaction force input when the hydraulic mechanism operates. It is possible to suppress the influence of the above from affecting the speed ratio control valve, and prevent the malfunction of the speed ratio control valve.

According to the fourth aspect of the present invention, the driven portion of the valve member including the sleeve and the like constituting the gear ratio control valve and the pushing member for pushing the driven member are provided outside the gear ratio control valve. Since it is provided, the valve member is driven by the pushing member without being constrained by the valve body, the spool, and the like that form the speed ratio control valve.

[0017]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS FIG. 1 shows a schematic structure of a power transmission device of an automobile having a shift control device for a toroidal type continuously variable transmission according to the present invention. This power transmission device has first and second power transmission paths 3 and 4 which are switched by a path switching clutch 2 connected to the output side of the engine 1. The first power transmission path 3 transmits the engine output to the wheel side via the reduction gear device 7, and in this embodiment, from the torque converter 5 to the wheel side via the forward / reverse switching device 6 and the reduction gear device 7. It is configured to transmit power. The second power transmission path 4 transmits the output of the engine 1 to the wheels via the toroidal type continuously variable transmission 8.

The torque converter 5 has its input shaft 5
pump cover 11 connected to a and this pump cover 11
A pump impeller 12 integrally formed with the turbine, a turbine runner 13 installed so as to face the pump impeller 12, and a hollow fixed shaft 15 with a one-way clutch 16 interposed therebetween.
And a stator 14 attached thereto. And
The input shaft 5a is connected to the output shaft of the engine 1, and the turbine shaft 17 serving as the output shaft of the torque converter 5 is connected to the turbine runner 13.
The space inside the pump cover 11 is filled with oil as a working fluid. A hollow rotary shaft 18 is connected to the pump impeller 12, and an oil pump 19 is attached to the rear end of the shaft 18.

The reduction gear device 7 has two planetary gear mechanisms 20 and 21 for rearward movement and forward movement, which are arranged coaxially with the turbine shaft 17, and both planetary gear mechanisms 20 and 21 are provided.
A sun gear 22 commonly used by 21 is coupled to the turbine shaft 17. The reverse planetary gear mechanism 20
Is a single pinion type, and the rotation of the sun gear 22 is transmitted to the ring gear 25 via the pinion 24 supported by the carrier 23. Also,
The carrier 23 is coupled to the hollow fixed shaft 15 and fixed to the casing 10, and the ring gear 25 is
It is connected to the output shaft 30 of the transmission via the reverse clutch 6a.

On the other hand, the forward planetary gear mechanism 21 is a double pinion type, and the rotation of the sun gear 22 is transmitted to the ring gear 28 via the inner pinion 26 and the outer pinion 27 supported by the carrier 23. Has become. The ring gear 28 is connected to the output shaft 30 via a forward clutch 6b and a one-way clutch 29.

The reverse clutch 6a and the forward clutch 6b constitute a forward / reverse switching device 6. When the reverse clutch 6a is engaged, the input from the turbine shaft 17 is transmitted to the output shaft 30 of the transmission via the reverse planetary gear mechanism 20.
When the forward clutch 6b is engaged, the input from the turbine shaft 17 is transmitted to the output shaft 30 via the forward planetary gear mechanism 21.

On the other hand, the toroidal type continuously variable transmission 8 of the second power transmission path 4 includes a pair of continuously variable transmission units 31, 32.
Both continuously variable transmission units 31, 3
2 is arranged on the output shaft 30 at a position adjacent to the reduction gear device 7. The continuously variable transmission unit 3
Reference numerals 1 and 32 denote a pair of disks 33 and 34, respectively, which are spaced apart in the axial direction, and these disks 33 and 34.
And a pair of power rollers 35 which are disposed between the two and are in sliding contact with both disks 33 and 34. The both power rollers 35 are installed to face each other with the output shaft 30 interposed therebetween.

One disc (output disc) 33 of the pair of discs is fixed to the output shaft 30,
The other disc (input disc) 34 is the output shaft 30.
It is supported so as to be rotatable relative to and axially movable. The power roller 35 is configured such that the tilt angle θ is changed by a hydraulic mechanism described later, and the gear ratios of the toroidal type transmission units 31 and 32 are changed accordingly.

That is, the gear ratio when the rotation of the input disk 34 is transmitted to the output disk 33 via the power roller 35 is as follows.
Is set in accordance with the ratio of the radius Ri of the portion slidingly contacting the disk to the radius Ro of the portion slidingly contacting the output disk 33, so that when the power roller 35 tilts and the sliding contacting point is displaced,
In response to this, the toroidal type continuously variable transmission unit 3
The gear ratios of 1 and 32 are changed.

The construction of the transmission units 31, 32 of the toroidal type continuously variable transmission 8 will be described with reference to FIGS. 2 and 3. Output disc 3 of one transmission unit 31
The bearing 3 is spline-fitted to the output shaft 30 of the transmission and is positioned by a ring-shaped positioning member 36 provided on the output shaft 30.
It is rotatably supported by the casing 10 of the transmission via 7. The output disc 33 of the other transmission unit 32 is positioned by a bearing 37 that is locked to a step formed on the output shaft 30 of the transmission.

An input cam 38, which is supported so as to be rotatable relative to the input disks 34 constituting the transmission units 31 and 32, is disposed between the input disks 34. The input cam 38 and the input disk 34
Between the cam roller 40 held by the retainer 39 and
Is installed. The cam roller 40 contacts the cam surfaces formed on the input disk 34 and the input cam 38, respectively, and transmits the driving torque input to the input cam 38 to the output disk 33 via the input disk 34 and the power roller 35. Is configured to.

The support member 4 for supporting the input disk 34 of the transmission unit 32 and the input cam 38.
An urging member 42, which is a disc spring for urging the input disks 34 of both transmission units 31 and 32 toward the output disk 33, is installed between the first and second transmission units 31 and 32.
A preload pressure is applied between the input disk 34 and the output disk 33 according to the urging force of.

Further, the transmission units 31, 32 are provided with a trunnion 44 having an eccentric shaft 43 for rotatably supporting the power roller 35. The trunnion 44 has a shaft member 45 projecting downward. It is installed. The trunnion 44 is supported by the upper surface of the casing 10 of the transmission through the spherical bush 46 and the connecting member 47 supporting the upper end of the trunnion 44, and the lower end of the trunnion 44 includes the spherical bush 48. It is supported by a partition wall 51 provided at the lower end of the casing 10 of the transmission via a supporting connecting member 49 and a supporting shaft 50.

A hydraulic cylinder 52 for operating the trunnion 44 is provided in the partition wall 51.
The hydraulic cylinder 52 has a pair of upper and lower hydraulic pressures defined by a pair of upper and lower pistons 53 and 54 supported by the shaft member 46 of the trunnion 44 and a wall plate 55 located between the pistons 53 and 54. It has chambers 56 and 57. When the hydraulic pressure is introduced into the upper hydraulic chamber 56, the trunnion 44 is pushed up by the upper piston 53, and when the hydraulic pressure is introduced into the lower hydraulic chamber 57, the trunnion 44 is pushed down by the lower piston 54. The power roller 35 is tilted accordingly.

At the center of the upper connecting member 47, a positioning hole 59 is formed in which a supporting shaft 58 projecting from the casing 10 of the transmission and a supporting member 59 fitted onto the supporting shaft 58 are installed. In addition, a positioning hole 61 is formed in the central portion of the lower connecting member 49, in which the spherical bearing 60 fitted on the support shaft 50 is installed. A lubricating oil supply port 55a communicating with a lubricating oil passage provided in the shaft member 45 is formed in the partition wall plate 55 between the pistons 53, 54. Then, the lubricating oil is led out from the lubricating oil passage 55a to the oil passage formed in the trunnion 44, whereby the support portion of the power roller 35 is lubricated.

Hydraulic chambers 56 and 57 of the hydraulic cylinder 52.
As shown in FIG. 4, a gear ratio control valve 62 that controls a gear ratio by controlling the supply and discharge of hydraulic pressure to and from a valve body 64 attached to the lower surface of a housing 63,
The valve body 64 has a three-layer structure including a sleeve 65 fitted in an installation hole formed in the valve body 64 and a spool 66 slidably supported in the sleeve 65. A spring 67, which constitutes a control actuator, and a gear reducer 6 are provided at one end of the spool 66.
8, a pin member 69, and a stepping motor 70 are arranged, and a mechanical feedback means 71 is installed at the other end of the spool 66.

A source pressure receiving port P1, a shift-up control port P2, and a shift-down control port P3 are formed in the valve body 64, and the sleeve 67 has the ports P1 to P3. A main port 72, a first port 73, and a second port 74 that are in constant communication with each other are formed at corresponding positions.

Further, the spool 66 is formed with an annular groove 75 which is in constant communication with the main port 72, and first and second land portions 76 and 77 located on the left and right sides thereof. The above first and second land portions 76, 77
Is configured to close the first and second ports 73 and 74, respectively, during non-shifting in which neither upshifting nor downshifting is performed.

A drive gear 78 of a gear reducer 68 is attached to the drive shaft of the stepping motor 70, and a driven gear 79 meshing with the drive gear 78 is arranged coaxially with the gear ratio control valve 62. ing. The driven gear 79
A collar portion 81 is formed with a screw portion 80 at the tip end thereof and a screw hole to be screwed into the screw portion 80.
Is provided.

The stepping motor 70 is attached to a side wall portion 82 provided at one end of the transmission casing 10 in order to secure an installation space for the gear reducer 68. Is offset above the installation portion of the gear ratio control valve 62. Further, in order to secure an installation space for the gear reducer 68, the shaft center of the gear ratio control valve 62 is arranged below the valve casing 64.

A pin member 69 is locked to the collar 81, and both ends of the pin member 69 are locked to grooves (not shown) formed in the valve body 64, whereby the collar 81 is locked. Is prevented from rotating. Then, when the gear reducer 68 is rotationally driven by the stepping motor 70, the collar 81 is screw-fed in its axial direction, and along with this, the sleeve 65 slides in its axial direction via the pin member 69. It is configured to be driven.

In response to the sliding displacement of the sleeve 65, the main port 72 of the sleeve 65 and the first port 73 of the valve body 64 via the groove 75 of the spool 66.
Alternatively, the source pressure receiving port P1 is communicated with the second port 74.
The shift control is executed by deriving the internal hydraulic pressure to the shift-up control port P2 or the shift-down control port P3.

The mechanical feedback means 71 is attached to a shaft member 45 projecting from one trunnion 44, a recess cam 84 attached to the lower end portion thereof, and a rotary shaft 85 at a predetermined position of the housing 63. And a swing lever 86. The one end portion 86a of the swing lever 86 abuts on the cam surface 87 of the recess cam 84, and the other end portion 86 of the swing lever 86 is in contact.
b is engaged with a slit formed at the end of the spool 66.

The precess cam 84 is composed of an eccentric cam having a downwardly constricted cam surface on its peripheral surface, and is attached at a position offset from the center of the shaft member 45 to the one side. And the sleeve 65 of the gear ratio control valve 62
The tip end of the spool 66 is engaged with the cam surface 87 of the precess cam 84 via the swing lever 86 by the urging force of the spring 67 installed therein.

In the above configuration, when the stepping motor 70 is rotationally driven at an angle corresponding to the target tilt angle (target gear ratio) in response to a control signal output from a control unit (not shown) during gear shifting, this rotational driving is performed. The force is transmitted to the collar 81 via the gear reducer 68, and the collar 81 is screw-fed, whereby the sleeve 6
5 moves in its axial direction. As a result, the main port 72 of the sleeve 65 communicates with the first port 72 or the second port 74 of the valve body 64 via the groove 75 of the spool 66, whereby the predetermined hydraulic chambers 56, 5 are formed.
The hydraulic pressure is supplied to 7, and the power roller 35 is displaced to the target tilt angle.

For example, when shifting up, when the stepping motor 70 rotates forward by a predetermined angle in response to the control signal, the sleeve 65 moves to the tip side, that is, the side where the feedback means 71 is installed. As a result, the main port 72 communicates with the first port 73 via the groove 75, the hydraulic pressure of the source pressure receiving port P1 is output to the shift-up port P2, and the shift-down port P3.
Is connected to the drain port, and this downshift port P
The hydraulic pressure in 3 is relieved.

Then, in accordance with the above hydraulic pressure, the hydraulic cylinder 5
By operating 2, the trunnion 44 and the shaft member 45 that support the power roller 35 are moved up and down, the power roller 36 is tilted accordingly, and the toroidal transmission 6 shifts to the speed increasing side. It has become.

On the other hand, at the time of downshifting, the stepping motor 70 reversely rotates by a predetermined angle in response to the control signal, and the sleeve 65 moves to the base end side, that is, the installation side of the stepping motor 70. As a result, the main port 72 communicates with the second port 74 via the groove 75, the hydraulic pressure of the source pressure receiving port P1 is output to the shift down port P3, and the shift up port P is generated.
2 communicates with the drain port, and the hydraulic pressure in the shift-up port P2 is relieved.

Then, in accordance with the above hydraulic pressure, the hydraulic cylinder 5
When 2 is operated, the trunnion 44 and the shaft member 45 are displaced up and down in the opposite direction to the above-described upshift, and the power roller 36 is tilted accordingly and the toroidal transmission 6 shifts to the deceleration side. At the time of this downshift, the sleeve 65 is biased toward the tip end side by the spring 67, so that the biasing force causes the sleeve 65 to move quickly and the shift responsiveness is ensured.

When the trunnion 44 and the shaft member 45 rotate in response to the rotation of the power roller 35, the precess cam 84 rotates accordingly. The rotation of the recess cam 84 causes one end of the swing lever 86 provided at the tip of the spool 66 to move to the cam surface 8.
The spool 66 is slid in the same direction as the moving direction of the sleeve 65 while sliding in the circumferential direction along the line 7.
When the recess cam 84 is displaced up and down in response to the vertical displacement of the shaft member 45, one end of the swing lever 6 is pushed by the recess cam 84 and slides vertically along the cam surface 87. The spool 66 is slidably driven.

Then, when the tilt angle of the power roller 35 reaches the target tilt angle, the movement amount of the spool 66 becomes equal to the movement amount of the sleeve 65, and the main port 72 is moved.
Then, the communication with the first port 73 or the third port 74 is blocked. As a result, the supply of hydraulic pressure to the hydraulic chambers 56 and 57 is stopped, the change of the tilt angle is prevented, and the power roller 35 is held at the target tilt angle.

As described above, the gear speed reducer 68 is provided between the valve member including the sleeve 65 of the gear ratio control valve 62 and the speed change motor including the stepping motor 70 that drives the valve member, and the gear speed reducer 68 is provided. Since the driving force of the stepping motor 70 is decelerated and transmitted to the sleeve 65, the sleeve 65 can be driven with a large driving force without increasing the capacity of the stepping motor 70. Therefore, even when the axis of the stepping motor 70 and the axis of the sleeve 65 do not exactly match,
It is possible to effectively prevent the occurrence of malfunction due to this and appropriately execute the gear ratio control of the toroidal type continuously variable transmission 8 by the stepping motor 70.

Further, as described above, the stepping motor 7
When 0 is arranged offset above the installation portion of the gear ratio control valve 62, the stepping motor 70 is arranged offset below or to the side of the gear ratio control valve 62. Since the installation space for the gear reducer 68 can be secured without the situation where the stepping motor 70 projects below or to the side of the transmission casing 10 as in the case, the toroidal type continuously variable transmission 8 can be secured. Can be made compact.

Further, when the shaft center of the transmission ratio control valve 62 is configured to be offset below the valve body 64, the gear reducer 68 is disposed by utilizing the installation portion of the valve body 64. Therefore, the transmission can be effectively made compact. Further, since the gear ratio control valve 62 can be installed at a position apart from the hydraulic mechanism including the hydraulic cylinder 52 of the toroidal type continuously variable transmission 8, the influence of the reaction force input during the operation of the hydraulic mechanism is affected. It is possible to effectively prevent the gear ratio control valve 62 from reaching the installation portion. Therefore, it is possible to effectively prevent the occurrence of a malfunction due to the deformation of the operating portion of the gear ratio control valve 62, and to appropriately perform the gear ratio control of the toroidal type continuously variable transmission 8.

Instead of the above structure, as shown in FIGS. 5 and 6, at one end of the sleeve 65 valve member,
A driven portion 89, which has a spherical projection at the tip, is formed of a protrusion protruding outward of the gear ratio control valve 62, and this driven portion 89 resists the urging force of an urging member made of a spring 67. It is also possible to dispose a pushing member composed of a cam 90 that pushes the gear ratio control valve 62 on the inner side of the gear ratio control valve 62, and install a stepping motor 70 that drives the cam 90 facing downward. The stepping motor 70 may drive the cam 90 to rotate the driven portion 89 to push the driven portion 89 to execute the gear ratio control of the toroidal type continuously variable transmission 8.

According to the construction in which the driving force of the cam 90 is used to drive the sleeve 65, the collar 81 provided in the gear ratio control valve 62 is screw-fed as described above. As in the case, it is possible to properly execute the above gear ratio control without causing a situation in which the screwing portion is fixed due to the deviation of the shaft center. Further, when the tip of the driven portion 89 is formed into a spherical shape as described above, there is some error in the installation angle between the axis of the driven member 89 and the axis of the cam 90. Also, it is possible to prevent the malfunction of the driven part 89 and to drive it properly.

Further, as shown in FIG. 7, a screw member 91 is screwed onto the output shaft of the stepping motor 70, and
A protrusion 93 is provided to be engaged with a slide groove 92 formed in the screw member 91. The protrusion 93 supports the screw member 91 in a slidable manner while restricting the rotation of the screw member 91. Accordingly, the screw member 91
The driven portion 89 protruding from the outer portion of the gear ratio control valve 62 may be pushed inward of the gear ratio control valve 62 by screwing.

In the case where the screw member 91 arranged on the outer side of the gear ratio control valve 62 is used to push the valve member including the sleeve 67, the gear ratio control valve 62 is Since the operation of the pushing member composed of the screw member 91 is not restricted by the constituent valve body 64, the sleeve 66, etc., the screw member 91
Can be fed by screw smoothly. Therefore,
Even when the axis of the stepping motor 70 and the gear ratio control valve 62 are not exactly aligned, it is possible to effectively prevent the screw member 91 from malfunctioning.

[0054]

As described above, according to the invention of claim 1, a gear reducer is provided between the valve member of the gear ratio control valve and the gear change motor for driving the valve member, and the gear reducer is provided. Since the drive force of the transmission motor is increased by the transmission to the valve member, the valve member can be driven with a large drive force without increasing the capacity of the transmission motor. Even when the axis of the transmission motor and the axis of the valve member do not exactly coincide with each other, the gear ratio control of the toroidal-type continuously variable transmission can be properly executed without causing malfunction.

Further, according to the second aspect of the present invention, since the shift motor is arranged offset above the installation portion of the gear ratio control valve, the shift motor is arranged below or to the side of the gear ratio control valve. It is possible to secure the installation space for the gear reducer without causing the situation in which the transmission motor protrudes below or to the side of the transmission casing as in the case where the transmission is offset. There is an advantage that the toroidal type continuously variable transmission can be effectively made compact.

Further, in the invention according to claim 3, since the shaft center of the gear ratio control valve is offset below the valve body, the gear reducer is arranged by using the installation portion of the valve body. It is possible to effectively reduce the size of the transmission by installing the transmission ratio control valve at a position away from the hydraulic mechanism of the toroidal-type continuously variable transmission. It is possible to suppress the influence of the reaction force exerted on the gear ratio control valve from being exerted, and to effectively prevent the occurrence of malfunctioning due to the deformation of the operating portion of the gear ratio control valve.

Further, according to a fourth aspect of the present invention, at one end of a valve member constituting the gear ratio control valve, a driven portion projecting outward of the gear ratio control valve and a gear ratio control for the driven portion are provided. A push member for pushing the valve is provided on the inner side of the valve, and the push member is configured to be driven by the speed change motor, which is caused by the deviation of the axis between the speed change motor and the speed ratio control valve. There is an advantage that the gear ratio control can be appropriately performed by driving the valve member without causing a malfunction.

[Brief description of drawings]

FIG. 1 is a schematic diagram showing an overall structure of a transmission including a shift control device for a toroidal-type continuously variable transmission according to an embodiment of the present invention.

FIG. 2 is a front sectional view showing a specific structure of the toroidal type continuously variable transmission.

FIG. 3 is a side sectional view showing a specific structure of a toroidal type continuously variable transmission.

FIG. 4 is a cross-sectional view showing a configuration of a shift control device.

FIG. 5 is a cross-sectional view showing another embodiment of the shift control device according to the present invention.

FIG. 6 is a bottom view of the shift control device.

FIG. 7 is a cross-sectional view showing yet another embodiment of the shift control device according to the present invention.

FIG. 8 is a cross-sectional view showing a conventional example of a shift control device.

[Explanation of symbols]

 8 Toroidal Type Continuously Variable Transmission 33 Output Disc 34 Input Disc 35 Power Roller 44 Trunnion (Supporting Member) 52 Hydraulic Cylinder (Hydraulic Mechanism) 62 Gear Ratio Control Valve 68 Gear Reducer 70 Stepping Motor (Shift Motor) 89 Driven Part 90 Cam (operating member) 91 Screw member (operating member)

Claims (4)

[Claims] 1. A power roller installed between an input disk and an output disk, a support member for rotatably supporting the power roller, a hydraulic mechanism for displacing the support member in its axial direction, and a hydraulic pressure for the hydraulic roller. In a toroidal type continuously variable transmission having a gear ratio control valve that supplies a control hydraulic pressure to a mechanism, a speed change motor that drives a valve member of the speed change control valve, and the drive force of the speed change motor is reduced to the valve member. A gear ratio control device for a toroidal type continuously variable transmission, characterized in that a transmission gear reduction device is provided. 2. The toroidal type stepless motor according to claim 1, wherein a speed change motor for driving a valve member of the speed ratio control valve is arranged at a position offset above the installation portion of the speed ratio control valve. Gear ratio control device for transmission. 3. The gear ratio control device for a toroidal type continuously variable transmission according to claim 2, wherein the shaft center of the gear ratio control valve is arranged below the valve body. 4. A power roller installed between an input disc and an output disc, a support member for rotatably supporting the power roller, a hydraulic mechanism for displacing the support member in its axial direction, and a hydraulic pressure for the hydraulic mechanism. In a toroidal type continuously variable transmission having a gear ratio control valve for supplying control hydraulic pressure to a mechanism, a driven part of a valve member is located outside an gear ratio control valve, and the valve member is provided with the driven part. And a pushing member that pushes the driven portion toward the inner side of the gear ratio control valve against the biasing force of the biasing member, and drives the pushing member. A gear ratio control device for a toroidal type continuously variable transmission, comprising: