JPH0634028A - Speed change ratio controller for continuously variable transmission - Google Patents

Abstract

PURPOSE:To speedily operate a speed change ratio control valve with certainty, and enhance responsiveness of a speed change in shift-down. CONSTITUTION:A sleeve 83 is fitted into a valve body 82 of a speed change ratio control valve V in a toroidal type continuously variable transmission C, and further, a spool 84 is fitted into the sleeve 83. The sleeve 83 is moved to a predetermined position by a stepping motor 88. Accordingly, an oil pressure is supplied from the speed change ratio control valve V to given oil pressure chambers 79a, 79b, 80a, 80b so that a roller tilting angle is changed, thus leading to a speed change. When the roller tilting angle reaches a target tilting angle, the supply of the oil pressure is stopped by a feedback means 90. Consequently, the roller tilting angle is kept at the target tilting angle. In shift-down, the sleeve 83 is moved by a spring 85, thereby enhancing responsiveness of the speed change.

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 continuously variable transmission.

[0002]

2. Description of the Related Art Generally, an automobile is provided with a transmission that changes the output torque of an engine according to a running state. In recent years, attention has been paid to a continuously variable transmission that can continuously change a gear ratio. There is. This is because the continuously variable transmission has the advantage that the gear ratio most suitable for the running condition can be obtained because the gear ratio can be arbitrarily set within the predetermined range. This is because it has the advantage of not occurring.

As a continuously variable transmission for an automobile, for example, a toroidal type continuously variable transmission is conventionally known. In such a toroidal type continuously variable transmission, normally, an input disk to which an engine torque is input, an output disk to output a torque to the driving wheel side, and both disks are rotationally contacted and the torque of one disk is transferred to the other disk. And a roller for transmitting to. Further, a roller supporting member that rotatably supports the roller is provided, and by displacing the roller supporting member in the axial direction, the tilting angle of the roller (contact position between the roller and both discs) is changed and the tilting angle is changed. A gear ratio corresponding to the turning angle can be obtained.

A hydraulic mechanism such as a hydraulic piston is provided for displacing the roller support member in its axial direction, and a gear ratio control valve is provided for supplying control hydraulic pressure to the hydraulic mechanism. As such a gear ratio control valve, for example,
A three-layer gear ratio control valve in which a sleeve capable of reciprocating in the valve axial direction is arranged in the valve body, and a spool capable of reciprocating in the valve axial direction is further arranged in the sleeve. A so-called three-layer valve is often used (see, for example, JP-A-62-283248 and JP-A-63-225754).

In such a three-layer valve, normally, a stepping motor that reciprocates the sleeve in the valve axial direction corresponding to a tilt angle setting value (gear ratio setting value) applied from the control unit, and a gear shifting operation Feedback means for moving the spool in the valve axis direction in accordance with the amount of change in the roller tilt angle (gear ratio) is provided.
Further, a spring is provided between the sleeve and the spool to elastically connect the two to each other.

In this configuration, for example, when changing the tilt angle (gear ratio) to a set value (target tilt angle), first, a pulse signal corresponding to the target tilt angle is applied to the stepping motor. By rotating the sleeve, the rotation moves the sleeve in the valve axis direction, and by this movement, the source pressure receiving port to which the source pressure is supplied and the control port connected to the hydraulic piston communicate with each other, and the hydraulic pressure is applied to the hydraulic piston. It will supply and tilt the rollers. Then, according to the actual change amount of the tilt angle, the spool is moved by the feedback means in the direction to close the communication, and when the tilt angle reaches the target tilt angle, the communication is cut off, and the roller is closed. The tilting angle is stopped and the tilting angle is maintained at the target tilting angle.

[0007]

Generally, in a stepping motor, if the drive frequency is increased, a control failure phenomenon commonly known as step-out may occur at a certain drive frequency. The step-out occurs at a lower drive frequency as the load torque of the stepping motor increases.

On the other hand, the gear ratio control valve used in the toroidal type continuously variable transmission is required to have high responsiveness at the time of gear shifting, and particularly high responsiveness at the time of downshifting (especially at kickdown). Therefore, it is necessary to move the sleeve to the target position quickly. And
In order to move the sleeve rapidly in this way, it is necessary to set the driving frequency of the stepping motor to a considerably high value. However, in this case, when the load torque applied to the stepping motor is large, step-out occurs, the gear shifting operation is disturbed, rapid gear shifting cannot be performed, and gear shifting responsiveness deteriorates.

The present invention has been made in order to solve the above-mentioned conventional problems, and it is possible to quickly and reliably operate a gear ratio control valve that supplies hydraulic pressure for gear shifting, and to provide a gear shift responsiveness. It is an object of the present invention to provide a gear ratio control device for a continuously variable transmission that can improve the transmission.

[0010]

To achieve the above object, a first aspect of the present invention is directed to a source pressure receiving port for receiving a source pressure from a hydraulic pressure supply source and a shift-up control port for outputting a control hydraulic pressure for shift-up. And a shift-down control port that outputs a control hydraulic pressure for down-shifting, a moving member that switches the communication state between the source pressure receiving port and both control ports by reciprocating movement, and the moving member in either of the reciprocating movement directions. A gear ratio control device for a continuously variable transmission, comprising a gear ratio control valve having a biasing means for biasing the gear ratio to one side, wherein the gear ratio control valve controls the gear ratio in a downshift direction. At this time, by changing the moving member in the urging direction of the urging means, the source pressure receiving port and the downshift control port are configured to communicate with each other. Providing a ratio control device.

According to a second aspect of the invention, in the gear ratio control device for a continuously variable transmission according to the first invention, the moving member can reciprocate in a predetermined direction within the valve body of the gear ratio control valve. A gear ratio control device for a continuously variable transmission, comprising: a sleeve; and a spool configured to reciprocate in the predetermined direction within the sleeve.

According to a third aspect of the present invention, in a gear ratio control device for a continuously variable transmission according to the first or second aspect, a drive member for displacing the sleeve in accordance with a target gear ratio and a displacement of the sleeve are provided. A gear ratio control device for a continuously variable transmission, comprising: feedback means for displacing the spool in a direction in which the above displacement of the sleeve is canceled in response to an actually occurring change in the gear ratio.

A fourth aspect of the present invention is a gear ratio control device for a continuously variable transmission according to any one of the first to third aspects,
A gear ratio control device for a continuously variable transmission, wherein the continuously variable transmission is a toroidal type continuously variable transmission.

[0014]

EXAMPLES Examples of the present invention will be specifically described below.
As shown in FIG. 2, the transmission TM of the automobile includes the first to
The output torque of the engine 1 including the fourth cylinders # 1 to # 4 is transmitted to the transmission output shaft 5 via the torque converter 2 (torque converter 2), the gear reduction mechanism 3 including the planetary gear system, and the forward / reverse switching mechanism 4. A first transmission unit for outputting to is provided. Furthermore, the output torque of the engine 1 is
A second transmission unit for outputting to the transmission output shaft 5 via the switching clutch 6 and the toroidal type continuously variable transmission C provided with the first toroidal type transmission mechanism 7 and the second toroidal type transmission mechanism 8 is provided. ing. When the switching clutch 6 is in the off state, torque is transmitted via the first speed change portion, and when it is in the on state, the torque is transmitted via the second speed change portion.

Since the torque converter 2 has a strong torque increasing function, the first speed change portion is mainly used when a relatively large speed change ratio (torque ratio) is required at the time of starting or accelerating. The speed changer is mainly used when driving is performed at a relatively small speed change ratio such as during high speed running.

The specific structure of the transmission TM will be described below. First, the first transmission unit will be described. The torque converter 2 substantially includes a pump impeller 12, a turbine liner 13, and a stator 14. The pump impeller 12 is mounted on the engine output shaft 1 via the pump cover 15.
1 and is configured to rotate integrally with the engine output shaft 11. Further, the pump impeller 12 has a first
A hollow shaft 16 is coaxially connected, and an oil pump 17 is provided at a rear end portion (right end portion in FIG. 2) of the first hollow shaft 16.
Are connected. The turbine liner 13 is coaxially connected to a torque converter output shaft 18 (turbine shaft). Further, the stator 14 is connected to the second hollow shaft 21 via a one-way clutch 19. The second hollow shaft 21 is fixed to the transmission case 22.

The torque converter 2 rotationally drives the turbine liner 13 with the oil discharged from the pump impeller 12, rectifies the oil repelled by the turbine liner 13 with the stator 14, and increases the rotation of the pump impeller 12 with the rectified oil. By repeating the above process, a torque larger than the torque of the engine output shaft 11 is output to the torque converter output shaft 18.

The gear reduction mechanism 3 substantially includes the sun gear 2.
5, a first pinion 26, a reverse ring gear 27, a second pinion 28, a forward ring gear 29, and a carrier 30. Here, the torque of the torque converter output shaft 18 is input to the sun gear 25. Further, the first and second pinions 26 and 28 are rotatably supported by the carrier 30. The carrier 30 is
It is fixed to the second hollow shaft 21 fixed to the transmission case 22.

Then, the sun gear 25 and the first pinion 26
The front part of the gear meshes with the first pinion 26 and the reverse ring gear 27 meshes with each other to form a planetary gear system having a reverse rotation reduction function. In this planetary gear system, a torque in the reverse rotation direction larger than the torque input to the sun gear 25 is output from the reverse ring gear 27.

The first gear meshing with the sun gear 25
The rear part of the pinion 26 and the second pinion 28 mesh with each other,
Further, the second pinion 28 and the forward ring gear 29 mesh with each other, and these form a planetary gear system having a forward rotation deceleration function. In this planetary gear system, the forward rotation direction torque that is larger than the torque input to the sun gear 25 is output from the forward ring gear 29.

The forward / reverse switching mechanism 4 is substantially composed of a reverse clutch 31, a clutch case 32, a forward clutch 33 and a one-way clutch 34.
The clutch case 32 is connected to the transmission output shaft 5 via an output disc 44f of the first toroidal transmission mechanism 7 described later. Here, when the reverse clutch 31 is engaged, the reverse ring gear 27
And the clutch case 32 are connected, and the torque of the reverse ring gear 27 is transmitted to the transmission output shaft 5. On the other hand, when the forward clutch 33 is engaged, the torque of the forward ring gear 29 is transmitted to the transmission output shaft 5.
The one-way clutch 34 runs idle when the rotation speed of the transmission output shaft 5 is higher than the rotation speed of the forward drive ring gear 29 to prevent the forward drive ring gear 29 from being reversely driven by the transmission output shaft 5. It is provided in.

Next, the second transmission section will be described. The second speed change section is substantially a toroidal type transmission including a switching clutch 6 for connecting and disconnecting torque input to the second speed change section, and first and second toroidal type speed change mechanisms 7 and 8. It is composed of a stepped transmission C and a gear mechanism 35 that transmits torque from the switching clutch 6 to the toroidal continuously variable transmission C. Here, the gear mechanism 35 sequentially engages the torque of the first hollow shaft 16, that is, the torque of the engine output shaft 11, when the switching clutch 6 is engaged, with the drive gear 37, the idle gear 38, and the driven gear 39. The torque of the bypass shaft 40 is further transmitted to the toroidal type continuously variable transmission C via the driving gear 41 and the driven gear 42 which are meshed with each other.

The toroidal type continuously variable transmission C includes a first toroidal type transmission mechanism 7 arranged on the front side (left side in FIG. 2) so as to surround the transmission output shaft 5 and a second toroidal type transmission mechanism arranged on the rear side. It is composed of a toroidal type speed change mechanism 8. Here, the first and second toroidal type speed change mechanisms 7 and 8 are arranged symmetrically in the front and rear, but since the configurations and functions of both are basically the same, the corresponding members are not included. The same reference numerals are given, and as a general rule, each member of the first toroidal type speed change mechanism 7 is given a subscript f, and each member of the second toroidal type speed change mechanism 8 is given a subscript r. However, since members such as rollers that are provided in twos in each toroidal transmission mechanism 7 and 8 cannot be distinguished only by the subscripts f and r, they are arranged on the left and right sides of the first toroidal transmission mechanism 7, respectively. The members are given subscripts a and b, and the members arranged on the left and right of the second toroidal transmission 8 are given subscripts c and d, respectively. Therefore, in the following, in principle, the description made for one member also applies to other members having the same number but different subscripts.

The first toroidal transmission mechanism 7 has a first input disk 43f loosely fitted around the transmission output shaft 5.
And the first output disc 44 fixed to the transmission output shaft 5.
f and first and second rollers 45a and 45b for transmitting the torque of the first input disk 43f to the first output disk 44f are provided. The first input disc 43f includes an input cam 48 to which the driven gear 42 is attached,
The input cam 48 is more strongly pressed against the first input disk 43f as the input torque to the first input disk 43f is increased by engaging with the first cam roller 49f.

The first and second rollers 45a and 45b are rotatable about the axis Y, and their peripheral surfaces are curved surfaces of the first input disk 43f and the first output disk 4 respectively.
It is in contact with the curved surface of 4f. Therefore, the torque (rotation) of the first input disk 43f is equal to that of the first and second rollers 45.
It is adapted to be transmitted to the first output disk 44f via a and 45b. Here, the gear ratio in torque transmission from the first input disk 43f to the first output disk 44f
(Torque ratio) is the radius R of the first output disk 44f at the position in contact with the first and second rollers 45a and 45b.
₂ and the ratio R ₂ / R ₁ of the radius R ₁ of the first input disk 43f.

The contact positions between the first and second rollers 45a and 45b and the two disks 43f and 44f are determined by the tilt angles of the first and second rollers 45a and 45b, as will be described later. By changing the tilt angle by a hydraulic mechanism which will be described later, the gear ratio can be arbitrarily set within a predetermined range. Of course, the second toroidal transmission mechanism 8 is basically the same as the first toroidal transmission mechanism 7.

The specific structure of the toroidal continuously variable transmission C will be described below. As shown in FIGS. 3 to 6, in the first toroidal transmission mechanism 7, the first output disk 44 is used.
f is spline-fitted to the transmission output shaft 5. Further, the first output disk 44f is rotatably supported by the transmission case 22 via the first bearing 47f while being positioned by the ring-shaped positioning member 46 fitted to the transmission output shaft 5. There is. The second
The second output disc 44r of the toroidal transmission 8 is
Positioned by a second bearing 47r that is provided between the enlarged diameter portion 5g formed integrally with the transmission output shaft 5 and the transmission case 22 and rotatably supports the transmission output shaft 5.

Between the first output disc 44f and the second output disc 44r, there are first and second input discs 43f, 43.
The r's are arranged close to each other so that their rear surfaces face each other, and an input cam 48 which is rotatable relative to the input disks 43f, 43r is arranged between the input disks 43f, 43r. Then, first and second cam rollers 49f and 49r are provided between the input cam 48 and the first and second input disks 43f and 43r, respectively. Here, the first and second cam rollers 49f and 49r are connected to the input cam 48 and the first and second cam rollers.
When the input disks 43f and 43r rotate relative to each other, it has a function of generating a pressing force that presses the first and second input disks 43f and 43r toward the first and second output disks 44f and 44r, respectively. , The first and second input disks 43f,
The greater the input torque to 43r, the first and second input discs 43f, 43f by the first and second cam rollers 49f, 49r.
The pressing force on 43r is designed to increase.

Between the first and second input disks 43f and 43r, the transmission output shaft 5 is loosely fitted, and both ends thereof are respectively connected to the first and second input disks 43f and 43r.
An engagement member 50, which is spline-fitted to the first and second input disks 43f and 43r, is arranged in a state of being brought into contact with the back surfaces of the second input disks 43f and 43r. A disc spring 51 is interposed between the engaging member 50 and the second input disc 43r, and the disc spring 51 preloads the first input disc 43f and the second input disc 43r in a direction in which they are separated from each other. It has become so. This disc spring 51
Contacts the back surface of the second input disk 43r and urges the second input disk 43r toward the second output disk 44r, and the urging reaction force of the second input disk 43r causes the first input disk 4r to pass through the engaging member 50.
3f is urged toward the first output disc 44f to apply a predetermined preload between the first input disc 43f and the first output disc 44f and between the second input disc 43r and the second output disc 44r. It is like this.

Next, a hydraulic mechanism for tilting the first to fourth rollers 45a to 45d will be described. The first toroidal type speed change mechanism 7 includes the first and second rollers 45a, 4a.
First and second trunnions 59 that rotatably support 5b, respectively.
a and 59b are provided. Then, by the first and second trunnions 59a and 59b, the first and second eccentric shafts 60a and 60a,
The first and second rollers 45a and 45b are rotatably supported via 60b. Also, the first and second trunnions 59
First and second shaft members 61a and 61b are attached to a and 59b, respectively, and extend downward (in a direction orthogonal to the transmission output shaft 5).

An upper connecting member 62 is attached to the transmission case 22 slightly above the first and second rollers 45a and 45b. On the other hand, the first and second rollers 45a, 4
Below 5b, a lower connecting member 63 is attached to the partition wall portion 53 fixed to the transmission case 22. Then, the first and the second formed on the upper connecting member 62
Due to the shaft holes 65a and 65b, the upper ends of the first and second trunnions 59a and 59b are respectively attached to the first and second upper spherical bushes 6.
It is rotatably supported via 4a and 64b. On the other hand,
First and second shaft holes 67a, 6 formed in the lower connecting member 63
7b, the first and second trunnions 59a and 59b, respectively.
Has a lower end portion rotatably supported via first and second lower spherical bushes 66a and 66b.

The lower portions of the first and second shaft members 61a and 61b are attached to the lower surface of the upper housing 55 by penetrating the opening 55g of the upper housing 55 attached to the lower surface of the partition wall portion 53. By the recess 56g of the lower housing 56, the first and second support bearings 54a, 54
It is rotatably supported via b.

In the partition wall portion 53, first and second hydraulic cylinders 76a and 76b are provided for operating the first and second trunnions 59a and 59b, respectively. These first and second hydraulic cylinders are provided. Each of 76a and 76b is vertically partitioned by a partition wall portion 53g that forms a part of the partition wall portion 53. The first and second upper pistons 77a and 77b are fitted in the upper half portions of the first and second hydraulic cylinders 76a and 76b, respectively, and the first and second lower pistons 78a and 78b are fitted in the lower half portions. It has been inserted. Therefore, the first and second upper pistons 77a, 77b
The first and second upper hydraulic chambers 79 by the partition wall 53g and the partition wall 53g, respectively.
a and 79b are defined, while the first and second lower pistons 78a,
The first and second lower hydraulic chambers 80a and 80b are defined by 78b and the partition 53g, respectively.

Here, the first and second upper hydraulic chambers 79a, 79b
When hydraulic pressure is applied to the first and second upper pistons 77a and 77b, the first and second trunnions 59a and 59a
b is displaced upward, while the first and second lower hydraulic chambers 8 are
When hydraulic pressure is applied to 0a and 80b, the first and second trunnions 5 are moved by the first and second lower pistons 78a and 78b.
9a and 59b can be displaced downward. Then, as described above, the first and second trunnions 59a, 5
When 9b is displaced in the vertical direction, the first and second rollers 45a, 45b are tilted according to the displacement amount, and the gear ratio of the first toroidal transmission mechanism 7 is changed.
Along with this, the first and second trunnions 59a and 59b are adapted to rotate around their axes. A gear ratio control device that controls the gear ratio by controlling the supply of hydraulic pressure to the first to fourth upper hydraulic chambers 79a to 79d and the first to fourth lower hydraulic chambers 80a to 80d, and the gear ratio. A specific shift operation by the control device will be described in detail later.

When the hydraulic mechanism fails, the first,
Both trunnions 59a, 59b (59c, 59d) are provided to back up the synchronization of the rotation of the second trunnions 59a, 59b.
The interlocking wires 57 and 58 are wound around.

The upper connecting member 62 has a first upper positioning hole 68f formed in the middle of the first shaft hole 65a and the second shaft hole 65b, and a middle of the third shaft hole 65c and the fourth shaft hole 65d. Second
An upper positioning hole 68r is formed. And the first
A first support portion 69f integrally formed with the transmission case 22 is inserted through the upper positioning hole 68f. The first
The first roller lubrication member 69f is attached to the support portion 69f using the first attachment member 71. Further, the upper spherical bearing 75r attached to the second support portion 69r is inserted into the second upper positioning hole 69r. The second roller lubrication member 70r is attached to the second support portion 69r using the second attachment member 71r. In this way, the upper connecting member 62 includes the first support portion 69f and the upper spherical bearing 7
It is fixed or positioned with respect to the transmission case 22 by 5r.

In the lower connecting member 63, a first lower positioning hole 72f is formed in an intermediate portion between the first shaft hole 67a and the second shaft hole 67b, and an intermediate portion between the third shaft hole 67c and the fourth shaft hole 67d. Second in the section
A lower positioning hole 72r is formed. And the first,
First and second lower spherical bearings 73f and 73r fixed to the upper surface of the partition wall portion 53 using the first and second mounting bolts 74f and 74r are provided in the second lower positioning holes 72f and 72r, respectively. It has been inserted. As described above, the lower coupling member 63 is fixed or positioned with respect to the partition wall portion 53 (transmission case side) by the first and second lower spherical bearings 73f and 73r.

Hereinafter, the first to fourth upper hydraulic chambers 79a to 79d will be described.
A gear ratio control device that controls the gear ratio by controlling the supply of hydraulic pressure to the first to fourth lower hydraulic chambers 80a to 80d will be described. In the gear ratio control device, the first
-The fourth upper hydraulic chambers 79a to 79d and the first to fourth lower hydraulic chambers 80a to 80d are connected to the gear ratio control valve V according to the operating state.
Therefore, the hydraulic pressure is supplied via a hydraulic circuit described later. As will be described later in detail, the gear ratio control valve V is a so-called three-layer valve in which a sleeve 83 is fitted in a valve body 82 and a spool 84 is fitted in the sleeve 83, which serves as an operating mechanism. spring 85, rotating member 86, provided with a pin member 87 or the like, is driven or controlled by a stepping motor 88 which operates in accordance with signals from a control unit (not shown), depending on the operating conditions, based on the pressure-receiving incoming port P ₁ through the hydraulic pressure (line pressure) upshift control port P ₂ or the control port P ₃ shift down received in, so as to supply a predetermined hydraulic pressure chamber 79A～79d, hydraulic pressure 81a~80d . The gear ratio control valve V is provided with feedback means 90.

As shown in FIGS. 5 to 7, the gear ratio control valve V
In the above, a part of the lower housing 56 serves as a valve body 82, and a sleeve 83 adapted to be capable of reciprocating in the axial direction of the valve body is fitted into the valve body 82. Spool 8 that can reciprocate in the valve body axial direction
4 is inserted. Here, the sleeve 83 is in communication with the main port 83i which is always in communication with the source pressure receiving port P ₁ , the first port 83j which is in communication with the upshift control port P ₂ and the continuous downshift control port P _3. Second port 83k is formed. Further, the spool 84 is formed with an annular groove 84i which is always in communication with the main port 83i, and first and second land portions 84j and 84k which are adjacent to the left and right of the groove 84i. Here, when the shift operation (shift up or shift down) is not performed, the first and second land portions 84j, 84k
Respectively close the inner openings of the first and second ports 83j, 83k (FIG. 7 shows this state).

The stepping motor 8 is attached to the side wall of the oil pan 36 attached to the lower end of the transmission case 22.
8, a rotary member 86 is fixed and connected to a rotary shaft 88i of the stepping motor 88. A male screw portion 86i is formed near the tip of the rotating member 86, and a female screw collar 92 is screwed onto the male screw portion 86i. A pin member 87 is fixed to the female screw collar 92, and both ends of the pin member 87 are
Locked by a pair of upper and lower groove portions 82i formed in the valve body 82, the female screw collar 92 does not rotate around the valve body axis. Therefore, when the rotating member 86 rotates around the valve body axis, the female threaded collar 92 moves in the valve body axis direction. Further, the pin member 87 causes the internal threaded collar 92 and the sleeve 83 to interlock in the axial direction of the valve body.

In the sleeve 83, between the female threaded collar 92 and the spool 84, a spring 85 is provided which applies a biasing force to the two so as to separate them from each other in the axial direction of the valve body. That is, the spring 85 constantly urges the internal threaded collar 92 in the stepping motor direction (leftward in FIG. 7). In the following description, this direction (leftward in FIG. 7) is simply referred to as “left”, and the opposite direction (rightward in FIG. 7) is simply referred to as “right”, unless otherwise specified. To Therefore, the sleeve 83 that is interlocked with the internal threaded collar 92 is always biased to the left. Of course, the spring 85 always urges the spool 84 to the right.

Here, when the rotating member 86 rotates with the rotation of the stepping motor 88, the female screw collar 92, the rotation of which is restricted by the pin member 87, is moved in the axial direction of the valve body, and along with this, the sleeve 83. Moves in the axial direction of the valve body, and the main port 83i
The through groove 84i, the first port 83j or the second port 83k and communicated, control based on pressure receiving incoming port P ₁ in the operating oil (hydraulic pressure) upshift port P ₂ or the shift-down control port P ₃ It is designed to output to.
Note that the hydraulic oil here is hydraulic oil accompanied by a predetermined hydraulic pressure, and the same applies below.

Specifically, for example, at the time of shift-up, the stepping motor 88 rotates forward at a rotation angle corresponding to the pulse, and the sleeve 83 moves rightward accordingly, and at this time, the main port 83i moves the groove 84i. Via the first port 83j, the hydraulic oil of the source pressure receiving port P ₁ is output from the upshift control port P ₂ . In this case, the hydraulic oil at the downshift control port P ₃ is released to the drain passage 99.

On the other hand, at the time of downshifting, the stepping motor 88 reversely rotates at a rotation angle corresponding to the pulse, and the sleeve 83 moves leftward accordingly, and the main port 8
3i communicates with the second port 83k through the groove 84i, and the working oil (hydraulic pressure) of the source pressure receiving port P ₁ is output from the downshift control port P ₃ . In this case, the hydraulic oil of the shift-up control port P ₂ is released to the drain passage 99. At the time of downshifting, since the sleeve 83 is constantly biased to the left by the spring 85, the torque load of the stepping motor 88 is reduced by this biasing force, and the drive limit speed becomes high (step-out occurs. It becomes difficult), and the sleeve 83 moves to the left quickly, so that the shift responsiveness is improved. At the time of upshifting, the biasing force of the spring 85 increases the torque load of the stepping motor 88, and therefore the drive limit speed of the stepping motor 88 decreases, which causes a slight decrease in gear shift response. , No responsiveness is required, so no trouble occurs.

The right end of the spool 84 and the first shaft member 61a
A feedback means 90 is provided between the lower end of the and. The feedback means 90 is provided with a recess cam 80 that is fixed to the first shaft member 61a and rotates integrally with the first shaft member 61a. The recess cam 80 has an inclined surface 80i. Further, the rotary shaft 101 provided at a predetermined position of the upper housing 55 has a first
The arm 102i and the second arm 102j are attached. Here, the tip portion of the first arm 102i engages with the inclined surface 100i of the recess cam 100, and the second arm 10i
The tip of 2j is engaged with a slit 84m formed at the right end of the spool 84.

The basic function of the feedback means 90 is the same as that of the ordinary feedback means that is generally used, so a detailed description thereof will be omitted. However, in general, the following process will be performed for each of the rollers 45a to 45d. The tilt angle (gear ratio) is maintained at the target tilt angle (target gear ratio). That is, at the time of gear shifting, when the stepping motor 88 rotates by an angle corresponding to the target tilt angle (target gear ratio), the sleeve 83 moves in the valve body axial direction by an amount corresponding to this rotation angle, and a predetermined hydraulic pressure is applied. Chamber 79a
~ 79d, 80a ~ 80d hydraulic pressure is supplied to each roller 45
a to 45d tilt to the target tilt angle. On the other hand, when the rollers 45a to 45d are tilted in this manner, the trunnions 59a to 59d and the shaft members 61a to 61d rotate correspondingly, and the precess cam 100 rotates accordingly. At this time, the precess cam 100 causes the first arm 102i to move.
The rotary shaft 101 is rotated via the rotary shaft 101, and the rotary shaft 101 moves the spool 84 via the second arm 102j in the same direction as the moving direction of the sleeve 83 to tilt the rollers 45a to 45d. When the angle reaches the target tilt angle, the movement amount of the spool 84 becomes equal to the movement amount of the sleeve 83, and here, the main port 8
The communication between 3i and the first port 83j or the second port 83k is cut off, the supply of hydraulic pressure to the hydraulic chambers 79a to 79d, 80a to 80d is stopped, the change of the tilt angle is stopped, and the tilt angle is changed. Is held at the target value tilt angle. However, when such feedback operation is performed, the second arm 102j
When the tip of the spool is displaced in the direction away from the spool 84 (that is, rightward), the spring 85 causes the spool 84 to follow the displacement of the second arm 102j.

A hydraulic circuit for supplying hydraulic oil (hydraulic pressure) from the hydraulic pressure supply source to the gear ratio control valve V and for supplying hydraulic oil from the gear ratio control valve V to the hydraulic chambers 79a to 79d, 80a to 80d. explain. As shown in FIG. 1, in such a hydraulic circuit, after the hydraulic oil in the oil pan 36 is discharged from the oil pump 17, after being adjusted to a predetermined pressure (source pressure) by the line pressure controller 122, The pressure is supplied to the source pressure receiving port P ₁ of the gear ratio control valve V via the source pressure supply passage 123.

The hydraulic oil output from the shift-up control port P ₂ flows into the common shift-up oil passage 130, and thereafter, the first to fourth branch shift-up oil passages 130a to 13th.
Od is supplied to the first lower hydraulic chamber 80a, the second upper hydraulic chamber 79b, the third lower hydraulic chamber 80c, and the fourth upper hydraulic chamber 79d, respectively. On the other hand, the hydraulic oil output from the shift-down control port P ₃ flows into the common shift-down oil passage 131, and thereafter, the first to fourth
A first upper hydraulic chamber 79a, a second lower hydraulic chamber 80b, respectively, via the branch shift down oil passages 131a to 131d.
The third upper hydraulic chamber 79c and the fourth lower hydraulic chamber 80d are supplied.

In such a gear ratio control device, at the time of downshifting, the sleeve 83 moves to the right in FIG. 1, the hydraulic oil of the source pressure receiving port P ₁ is output from the downshift control port P ₃ , and this hydraulic oil is used. The first upper hydraulic chamber 79a, the second lower hydraulic chamber 80b, and the third upper hydraulic chamber 7
9c and the fourth lower hydraulic chamber 80d. It should be noted that the gear ratio control valve V in FIG. 1 has a left-right positional relationship opposite to that of the gear ratio control valve V in FIGS. 5 and 7.

At this time, the first and third trunnions 59a, 5
9c is displaced upward, and the second and fourth trunnions 59b, 59
d is displaced downward, and the first to fourth rollers 45a to 45d are decelerated by the displacement of the trunnions 59a to 59d. At this time, the trunnions 59a to 59d and thus the shaft members 61a to 61d rotate, but the first shaft member 6
With the rotation of 1a, the precess cam 100 moves the inclined surface 1
00i and the first arm 102i in contact with the rotary shaft 10
1 and the second arm 102j, the spool 84
The source pressure receiving port P ₁ and the shift down control port P ₃
Move it to the right until it blocks the communication. In this way, the tilt angle is maintained at the target tilt angle. Here, when the sleeve 83 moves rightward, the spring 83 biases the sleeve 83 rightward, so that the torque load of the stepping motor 88 is reduced,
The shift responsiveness is enhanced as described above.

On the other hand, when shifting up, the sleeve 83
1 moves to the left in FIG. 1, the hydraulic oil of the source pressure receiving port P ₁ is output from the shift-up control port P ₂ , and the hydraulic oil is supplied to the first lower hydraulic chamber 80a and the second upper hydraulic chamber. 79b, a third lower hydraulic chamber 80c, and a fourth upper hydraulic chamber 79
Supplied to d and. At this time, the first and third trunnions 59
a, 59c are displaced downward, and the second and fourth trunnions 59b,
59d is displaced upward, and the trunnions 59a to 59
Due to the displacement of d, the first to fourth rollers 45a to 45d change to the speed increasing side (overdrive side). At this time, each trunnion 59a-59d (each shaft member 61a-61d) rotates,
With the rotation of the first shaft member 61a, the recess cam 10
0 is the first arm 102i in contact with the inclined surface 100i
The rotary shaft 101 and the second arm 102j are actuated, but in this case, unlike the case of the above downshift, the direction in which the tip end of the second arm 102j separates from the spool 84 (in FIG. Displace to the left). Therefore, the spool 84 is moved leftward in FIG. 1 by the urging force of the spring 85, and is moved leftward until the communication between the source pressure receiving port P ₁ and the upshift control port P ₂ is blocked. In this way, the tilt angle is maintained at the target tilt angle.

Although a three-layer valve is used as the gear ratio control valve V in the above embodiment, a two-layer valve as shown in FIG. 8 may be used as the gear ratio control valve. As shown in FIG. 8, in the gear ratio control valve V ′ having a two-layer structure, no sleeve is provided, and the spool 84 is directly fitted in the valve body 82. The main port 82i and the first and second ports 82j, 82j having the same functions as the main port 83i and the first and second ports 83j, 83k of the gear ratio control valve V shown in FIG.
82k is formed on the valve body 82.

The driving member 110 is fixed and connected to the rotary shaft 88i of the stepping motor 88.
The pin member 1 is provided at the rear end of the spool 84 (the left end in FIG. 8).
11 is attached, and the pin member 111 is fitted in the slit 110i formed in the driving member 110. Here, when the stepping motor 88 rotates, the drive member 110 and the pin member 111 rotate, and the spool 84 rotates accordingly. And
Inside the valve body 82, a spring 85 ′ is provided between the spool 84 and the stepping motor 88 to apply a biasing force to the spool 84 and the stepping motor 88 in a direction of separating them from each other. Further, a female screw portion 84m is formed at the tip portion (right end portion in FIG. 8) of the spool 84. Then, a transmission member 113 having a male screw portion 113i screwed to the female screw portion 84m is provided, and the second arm 102j is in contact with the tip end portion (the right end portion in FIG. 8) of the transmission member 113.

In the gear ratio control valve V'shown in FIG. 8, when the stepping motor 88 rotates, the rotating member 110, the pin member 111 and the spool 84 rotate integrally, but the female screw portion 84m and the male screw portion 113i are screwed together. Therefore, the spool 84 is moved in the axial direction of the valve body by the transmission member 112, whereby the source pressure receiving port P ₁
And the communication state with the shift-up control port P ₂ or the shift-down control port P ₃ is controlled, and the same function as in the case of the gear ratio control valve V shown in FIG. 7 is exerted.

At the time of downshifting, the spool 84 is moved to the right in FIG. 8 by the transmission member 113 as the stepping motor 88 rotates.
The main port 82i is communicated with the second port 82k through the groove 84i, and the hydraulic oil of the source pressure receiving port P ₁ is output to the downshift control port P ₃ at this time. Since the spring 85 ′ urges the spool 84 to move to the right, the torque load on the stepping motor 88 is reduced and the gear shift response is improved, as in the gear ratio control valve V shown in FIG. .

[0056]

According to the first aspect of the invention, since the movement of the moving member is urged by the urging force of the urging means at the time of downshifting, the movement resistance of the moving member is reduced and the time required for the movement is reduced. Is shortened and the shift response is improved.

According to the second invention, basically, the same operation and effect as those of the first invention can be obtained. Furthermore, since the transmission ratio control valve is a three-layer valve in which the sleeve is arranged in the valve body and the spool is arranged in the sleeve,
The precision of hydraulic control is improved.

According to the third invention, basically, the same operation and effect as those of the first or second invention can be obtained. further,
Since the return spring provided in the feedback means can be used as the urging means and the sleeve can be urged in the moving direction during downshifting, it is not necessary to provide a special urging means.

According to the fourth invention, basically, the same operation and effect as any one of the first to third inventions can be obtained. Furthermore, since the continuously variable transmission is a toroidal type continuously variable transmission with high practicality, the effect of improving the shift response is particularly effective.

[Brief description of drawings]

FIG. 1 is a diagram showing a hydraulic circuit of a hydraulic mechanism of a toroidal-type continuously variable transmission according to the present invention.

FIG. 2 is a system configuration diagram of a transmission including a toroidal-type continuously variable transmission according to the present invention.

FIG. 3 is an explanatory plan cross-sectional view of a toroidal type continuously variable transmission according to the present invention.

FIG. 4 is a side elevation cross-sectional explanatory view of the toroidal type continuously variable transmission shown in FIG.

FIG. 5 is an AA of the toroidal type continuously variable transmission shown in FIG.
It is a vertical section cross-section explanatory drawing.

6 is a BB of the toroidal type continuously variable transmission shown in FIG.
It is a vertical section cross-section explanatory drawing.

FIG. 7 is a side sectional view showing a transmission ratio control valve having a three-layer structure including a sleeve.

FIG. 8 is a side view illustrating a transmission ratio control valve having a two-layer structure without a sleeve.

[Explanation of symbols]

C ... toroidal type continuously variable transmission V, V '... transmission ratio control valve P ₁ ... original pressure receiving incoming port P ₂ ... shift-up control port P ₃ ... shift-down control port 17 ... oil pump 82 ... valve body 83 ... Sleeve 84 ... Spool 85,85 '... Spring 88 ... Stepping motor 90 ... Feedback means

Claims (4)

[Claims] 1. A source pressure receiving port for receiving a source pressure from a hydraulic pressure supply source, a shift up control port for outputting a shift up control hydraulic pressure, and a shift down control port for outputting a shift down control hydraulic pressure. A gear ratio control valve including a moving member that switches the communication state between the source pressure receiving port and both control ports by reciprocating movement, and a biasing means that biases the moving member to one side in the reciprocating direction thereof. A transmission ratio control device for a continuously variable transmission, wherein the transmission ratio control valve moves the moving member in the urging direction of the urging means when controlling the gear ratio in the downshift direction. The transmission ratio control device for a continuously variable transmission, characterized in that the source pressure receiving port and the downshift control port are communicated with each other. 2. A gear ratio control device for a continuously variable transmission according to claim 1, wherein the moving member is capable of reciprocating in a predetermined direction within a valve body of the gear ratio control valve, and a sleeve. A gear ratio control device for a continuously variable transmission, comprising: a spool capable of reciprocating in the predetermined direction within the sleeve. 3. A gear ratio control device for a continuously variable transmission according to claim 1 or 2, wherein a drive member for displacing the sleeve in accordance with a target gear ratio, and an actual drive member according to the displacement of the sleeve. A gear ratio control device for a continuously variable transmission, comprising: feedback means for displacing the spool in a direction in which the displacement of the sleeve is canceled in response to a change in the generated gear ratio. 4. The gear ratio control device for a continuously variable transmission according to any one of claims 1 to 3, wherein the continuously variable transmission is a toroidal type continuously variable transmission. Gear ratio control device for continuously variable transmission.