JP3372285B2 - Toroidal type continuously variable transmission - Google Patents

Description

Description: BACKGROUND OF THE INVENTION The present invention relates to a clutch provided on an output side.
The clutch pressure of this clutch is
Control using the pressure generated by the hydraulic mechanism
Related to a toroidal type continuously variable transmission
is there. [0002] In recent years, compared to a belt-type continuously variable transmission,
High durability and capable of transmitting large torque
Therefore, a toroidal-type continuously variable transmission is receiving attention.
In a toroidal type continuously variable transmission, the input side cone
Power drop located between the
The input disk and the output by swinging the
The gear ratio with the force disk is changed.
Such toroidal-type continuously variable transmissions often use hydraulic pressure.
It is combined with the torque converter used
However, in order to increase the transmission efficiency, the torque converter
It is conceivable to use a starting clutch instead. The starting clutch is disclosed in Japanese Patent Application Laid-Open No. 62-25155.
Equivalent to the forward or reverse clutch described in JP-A-9
And the rotational output from the engine without going through the fluid coupling
Switch between connecting the wheel to the wheel and disconnecting the wheel
It has been done. In such a starting clutch,
Connect the clutch smoothly and start the vehicle smoothly
In order to make a full connection via the half-clutch state
There must be. To do this, push the starting clutch
The clutch pressure, which is the applied pressure, is a time waveform as shown in FIG.
Need to be That is, the clutch oil pressure is
Via the shelf pressure from the state of zero to the state of half clutch,
Must not change so that it rises to the pressure required for full connection
No. The shelf pressure in the half-clutch state is shown in FIG.
As shown, the higher the input torque, the higher the setting.
You. [0004] Such a shelf pressure is generated.
Conventionally, as shown in FIG.
Control valve is controlled by a linear solenoid valve
It is controlled by an electronically controlled hydraulic valve such as
Was. However, such a method increases the number of parts.
Cost and complexity of the control system
There was a problem. Also, the engine torque at the start
Timing of rising time and rising time of clutch pressure
Tuning such as adjusting the
There was also the problem of complication. Accordingly, the present invention has been made in view of the above-mentioned problems.
It is intended for complex equipment.
Without the need for positioning or cumbersome adjustments.
Equipped with a clutch that can control hydraulic pressure to an appropriate value
A toroidal-type continuously variable transmission. [0006] To solve the above-mentioned problems, the present invention
To achieve the target, toroidal type continuously variable transmission of the present invention
Is a cone-shaped input disk to which power is input, and
It is arranged coaxially with the force disk and outputs power to the outside
A cone-shaped output disc, the input disc and the output
Between the opposing cone faces of the force disc,
Between the cone face of the force disc and the cone face of the output disc.
By rotating while touching both, the input disk
Power roller for transmitting torque of the motor to the output disk
And tilting the power roller so that the input disk is
The power for changing the speed ratio of the output disc
Roller in the direction substantially perpendicular to the rotation axis of the output disk
A hydraulic mechanism to be moved and connected to the output disk side
A starting clutch, wherein the hydraulic mechanism is connected to the hydraulic mechanism.
Using the pressure difference between the two hydraulic chambers provided,
Troy made to generate the driving force to move the la
In a dull type continuously variable transmission, the solenoid valve
Pressure control valve driven by pilot pressure generated
Control the hydraulic oil discharged from the oil pump
A line pressure is generated, and the line pressure is applied to the power roller.
Move the hydraulic mechanism and the clutch pressure of the starting clutch.
Configuration to supply to clutch pressure control valve for controlling
And the clutch pressure control valve
The hydraulic pressures of the two hydraulic chambers are derived, and the difference between the hydraulic pressures of the two hydraulic chambers is calculated.
Pressure to control the control pressure of the clutch pressure control valve.
It is characterized by having a configuration of As described above, according to the present invention, the toroidal type
Since the step transmission is configured, it operates as follows.
In other words, the rotational force of the input disk is applied to the power roller.
These forces act as reaction forces when transmitting to the output disc.
Try to move the power roller in the tangential direction of the disk
Force acts. This force is proportional to the transmission torque. That
The two oils of the hydraulic mechanism that moves and drives the power roller
In the pressure chamber, to generate a force that balances this reaction force
Is generated, and this differential pressure is proportional to the transmission torque.
Become. Therefore, the clutch pressure is controlled using this differential pressure.
If the control pressure of the control valve is adjusted, complicated
Originally without using a near solenoid valve
Transmission using the necessary hydraulic mechanism for driving the power roller
The clutch control pressure proportional to the torque can be obtained.
You. Hereinafter, a preferred embodiment of the present invention will be described with reference to the accompanying drawings.
This will be described in detail with reference to the accompanying drawings. FIG. 1 shows an embodiment of the present invention.
It is sectional drawing which shows the structure of a toroidal type continuously variable transmission. FIG.
, The toroidal type continuously variable transmission C is
Transmission output extending in the front-rear direction of the vehicle equipped with
It is arranged on the front side (left side in the figure) so as to surround the shaft 5
A first toroidal transmission 7 and a second toroidal transmission mechanism 7
A toroidal transmission mechanism 8. And the first
And the second toroidal transmission mechanism 7, 8
Engine torque input from the input cam 48
However, these first and second toroidal transmission mechanisms 7 and 8
The speed is reduced or increased through the
It is. In this way, the toroidal transmission mechanism is divided into two
By doing so, all to one toroidal transmission mechanism
Torque capacity compared to transmitting torque
The transmission can be downsized while taking large amounts. Here, first and second toroidal type transmissions
Structures 7 and 8 are arranged so as to be symmetrical back and forth,
Since both configurations and functions are basically the same,
The same reference numerals are used for members, and in principle, the first toroidal type
Each member of the speed change mechanism 7 is given a suffix f, and the second toroider
Each member of the transmission mechanism 8 is given a subscript r. However,
Two to each toroidal transmission mechanism 7, 8 such as rollers
For the provided members, only subscripts f and r are used
Since it cannot be separated, the right and left of the first toroidal transmission mechanism 7
Subscripts “a” and “b” are given to each of the arranged members, and a second toroider is provided.
Subscripts on each member arranged on the left and right of the
Add c and d. Therefore, in the following, certain members are not considered.
The explanations given are, in principle, identical in number and differ only in the suffix.
The same applies to other members. The first toroidal transmission mechanism 7 includes a transmission
First input disk 43f loosely fitted around output shaft 5
And a first output disk 44 fixed to the transmission output shaft 5
f and the torque of the first input disk 43f to the first output disk.
First and second power rollers 45 for transmission to a disc 44f
a, 45b are provided. Then, the first input disk
43f is an imp formed with the driven gear 42 formed on the outer periphery.
Engagement with the cam 48 via the first cam roller 49f.
When the input torque to the first input disk 43f is large,
In this case, the first input disk 43f is connected to the first and second power
Rollers 45a and 45b.
I have. This pressing force is applied to the first input disk 43f and the
One output disk 44f and first and second power rollers 45
a, 45b between the first input disk and the first input disk.
The rotational force of the roller 43f is reduced by the first and second rollers 45a, 45a.
b to the first output disk 44f. First and second power rollers 45a, 45b
Can be rotated around the axis Y, respectively.
With the conical curved surface of the first input disk 43f.
Abutting against the cone-shaped curved surface of the first output disk 44f;
I'm making it. For this reason, the rotation torque of the first input disk 43f is
Luk passes through the first and second power rollers 45a and 45b.
Then, it is transmitted to the first output disk 44f. Here the first
Time from input disk 43f to first output disk 44f
The transmission ratio (torque ratio) in transmitting the rolling force is the first and the second.
2 At the position in contact with the power rollers 45a, 45b
Radius R1 of the first input disk 43f and the first output disk 43f.
Determined by the ratio R2 / R1 of the radius R2 of the disc 44f.
You. The first and second rollers 45a, 45
b and the discs 43f, 44f are in contact with the first
And the second rollers 45a and 45b in a plane parallel to the plane of the drawing.
It is determined by the tilt angle, and the hydraulic machine described later
By changing this tilt angle depending on the structure, the gear ratio can be adjusted.
It can be set arbitrarily within a certain range. next,
The configuration of the toroidal transmission C will be described more specifically. As shown in FIG. 1, a first toroidal transmission mechanism
7, the first output disk 244f outputs the transmission output
The shaft 5 is spline-fitted. In addition, the first output disk
44f is a ring-shaped position fitted to the transmission output shaft 5.
With the positioning by the positioning member 46, the first base
Rotated by the transmission case 22 via the ring 47f
It is freely supported. The second toroidal type transmission
The second output disk 44r of the structure 8 is provided outside the transmission output shaft 5.
The enlarged diameter portion 5g formed integrally with the circumference and the transmission case 22
And rotatably supports the transmission output shaft 5.
It is positioned by the second bearing 47r. The first output disk 44f and the second output disk
Between the first and second input disks 43
f, 43r are arranged close so that the back faces each other.
Between the input disks 43f and 43r.
The first and second cam rollers 49f and 49r are interposed respectively.
I have. Here, the first and second cam rollers 49f, 49r
The input cam 48 and the first and second input disks 4
When the 3f and 43r are relatively rotated, the first and second inputs
The disks 43f and 43r are connected to the first and second output
Generates a pressing force that presses against the discs 44f and 44r.
Having a function, the first and second input disks 43f,
The larger the input torque to 43r, the more the first and second power
First and second input disks by the first and second rollers 49f and 49r.
The pressing force on the holes 43f and 43r is increased.
ing. [0015] First and second input disks 43f, 43r
In between, it is loosely fitted to the transmission output shaft 5 and both ends are
Abuts on the back surfaces of the first and second input disks 43f and 43r.
The first and second input disks 43f, 43r
And the engagement member 50 which is spline-fitted with the
You. The engagement member 50 and the second input disk 43
r, a disc spring 51 is interposed therebetween.
The first input disk 43f and the second input disk 43r
Are preloaded in a direction away from each other.
You. The disc spring 51 is located on the back of the second input disc 43r.
And urges it toward the second output disk 44r.
On the other hand, by the biasing reaction force, via the engagement member 50,
Move the first input disk 43f to the first output disk 44f
The first input disk 43f and the first output disk 4
4f, and between the second input disk 43r and the second output disk.
A predetermined preload is applied to the disk 44r.
ing. The transmission output shaft 5 has a starting clutch.
150 are connected. Next, the first to fourth power rows
Hydraulic mechanisms for tilting the rollers 45a to 45d respectively.
This will be described with reference to FIGS. 1st toroidal
The first and second power rollers 45a,
First and second trunnions for rotatably supporting 45b, respectively
59a and 59b are provided. And the first and
The first and second trunnions 59a and 59b respectively
And the first and second paths via the second eccentric shafts 60a and 60b.
The word rollers 45a and 45b are rotatably supported.
You. Also, the first and second trunnions 59a, 59b
Are respectively attached to the lower side (the direction orthogonal to the transmission output shaft 5).
First and second shaft members 6 extending so as to extend in the
1a and 61b are attached. First and second power rollers 45a, 45b
Slightly above, the transmission case 22
A binding member 62 is attached. On the other hand, the first and second
Below the power rollers 45a and 45b, the transmission
The partition wall 53 fixed to the case 22 has a lower connecting portion.
Material 63 is attached. And the upper connecting member 6
2 through the first and second shaft holes 65a and 65b.
Above the first and second trunnions 59a, 59b, respectively.
The ends are first and second upper spherical bushes 64a, 64b.
And is rotatably supported via the. On the other hand, the lower connecting part
In the first and second shaft holes 67a, 67b formed in the material 63,
Therefore, the first and second trunnions 59a and 59b respectively
The lower end portion is provided with first and second lower spherical bushes 66a, 66.
It is rotatably supported via b. The first and second shaft members 61a, 61b
The lower part is an upper attached to the lower surface of the partition wall 53.
Through the opening 55g of the housing 55, the upper
Lower housing 56 attached to the lower surface of jing 55
56g of the first and second support bearings 5
It is rotatably supported via 4a and 54b. Partition
The first and second trunnions 59a, 59a,
First and second hydraulic cylinders for operating 59b
76a and 76b are provided, and these first and second hydraulic pressures are provided.
Each of the cylinders 76a and 76b is a part of the partition wall 53.
The upper and lower parts are separated by a partition wall 53g. So
The first and second hydraulic cylinders 76a, 76b
The first and second upper pistons 77a and 77b are respectively provided in the portions.
The first and second lower pistons 78a,
78b is fitted. For this reason, the first and second upper sides
The pistons 77a and 77b and the partition wall 53g respectively
First and second upper hydraulic chambers 79a, 79b are defined,
The first and second lower pistons 78a, 78b and the partition 5
3g, the first and second lower hydraulic chambers 80a, 80
0b is defined. Here, the first and second upper hydraulic chambers 79a, 79a,
When the hydraulic pressure is applied to 79b, the first and second upper
The first and second trani are provided by pistons 77a and 77b.
The ONs 59a and 59b are displaced upward, while the first
And hydraulic pressure was applied to the second lower hydraulic chambers 80a and 80b.
Sometimes, the first and second lower pistons 78a, 78b
Therefore, the first and second trunnions 59a and 59b are directed downward.
When it is displaced. And like this
The first and second trunnions 59a, 59b are vertically
When displaced, first and second
The power rollers 45a and 45b are tilted, and the first toroidal
The gear ratio of the mold transmission mechanism 7 changes. Also,
Accordingly, the first and second trunnions 59a and 59b are
It rotates around its axis. The first to fourth upper hydraulic chambers 79a to 79
d and the hydraulic pressure to the first to fourth lower hydraulic chambers 80a to 80d.
Transmission ratio control that controls the transmission ratio by controlling the supply
Control device and specific speed change operation by this speed ratio control device
The work will be described in detail later. Also, when the hydraulic mechanism fails, etc.
Of the first and second trunnions 59a, 59b.
Both trunnions 59 to back up the synchronization
a, 59b (59c, 59d) have interlocking wires 57,
58 are wound. The upper connecting member 62 has a first shaft hole 65a.
A first upper positioning hole 68f is provided at an intermediate portion of the second shaft hole 65b.
Formed at an intermediate portion between the third shaft hole 65c and the fourth shaft hole 65d.
A second upper positioning hole 68r is formed. And
The transmission case 22 is integrated with the first upper positioning hole 68f.
The formed first support portion 69f is inserted. In addition,
The first roller lubrication member 70f is provided on the first support portion 69f.
It is mounted using one mounting member 71. Also,
2 In the upper positioning hole 69r, fit the second support 69r.
The attached upper spherical bearing 75r is inserted. What
The second support portion 69r has a second roller lubrication member 70r.
Are attached using the second attachment member 71r.
Thus, the upper connecting member 62 is connected to the first support 69f.
The transmission case 22 is formed by the upper spherical bearing 75r.
It is fixed or positioned. The lower connecting member 63 has a first shaft hole 67a.
A first lower positioning hole 72f is provided at an intermediate portion of the second shaft hole 67b.
Formed at an intermediate portion between the third shaft hole 67c and the fourth shaft hole 67d.
A second lower positioning hole 72r is formed. And
In the first and second lower positioning holes 72f, 72r, respectively,
First and second mounting bolts 74 are provided on the upper surface of the partition wall 53.
f, 74r, the first and second lower spherical axes fixed using
Receivers 73f and 73r are inserted. Thus, below
The side connecting member 63 includes first and second lower spherical bearings 73.
f, 73r, the partition wall 53 (transmission case)
Side). Hereinafter, the first to fourth upper hydraulic chambers 79a to 79 will be described.
d and the hydraulic pressure to the first to fourth lower hydraulic chambers 80a to 80d.
Transmission ratio control that controls the speed ratio by controlling the supply
The control device will be described. In this gear ratio control device
The first to fourth upper hydraulic chambers 79a to 79d and the first to fourth
4 Change to the lower hydraulic chambers 80a to 80d according to the operating conditions.
From the speed ratio control valve V, the hydraulic pressure
Is supplied. This speed ratio control valve V is
As will be described in detail later, three
And the spool 8 is further inserted into the sleeve 83.
4 is a so-called three-layer valve in which the operating mechanism is mounted.
Including a pulling 85, a rotating member 86, a pin member 87, and the like.
Signal from a control unit (not shown)
Therefore, the drive is controlled by the stepping motor 88 which operates.
To the source pressure receiving port P1 according to the operating condition.
Control pressure for shifting up the received hydraulic pressure (line pressure).
Port P2 or the control port P3 for downshifting
Oil in predetermined hydraulic chambers 79a to 79d and 81a to 80d.
It is designed to supply pressure. Note that the speed ratio control valve V
Is provided with feedback means 90. As shown in FIGS. 3 to 5, the transmission ratio control valve V
In this case, part of the lower housing 56 is
2, and a valve body is provided in the valve body 82.
Sleeve 83 capable of reciprocating in the di-axis direction
Is inserted into the sleeve 83, and the valve body shaft is
A spool 84 that can reciprocate in the linear direction fits
Have been. Here, the sleeve 83 always receives the original pressure.
Main port 83i communicating with port P1
First port 83j communicating with the to-up control port P2
And a second port which is always in communication with the shift-down control port P3.
A port 83k is formed. Also, the spool 84
Has an annular glue constantly communicating with the main port 83i.
And the first adjacent to the right and left sides of the groove 84i and the groove 84i, respectively.
And second lands 84j and 84k. here
To change gear (shift up or down is performed
If not, the first and second land portions 84j, 84
k is the inside opening of the first and second ports 83j and 83k, respectively.
The mouth is closed (Fig. 5 shows this state
There). At the lower end of the transmission case 22
A stepping motor 8 is provided on the side wall of the oil pan 36.
8 is attached, and the rotation of the stepping motor 88 is
A rotating member 86 is fixedly connected to the shaft 88i. So
Then, a male screw portion 86i is provided near the tip of the rotating member 86.
The male screw portion 86i is formed with a female screw collar 92.
It is screwed. The collar 92 with a female screw has a pin member
87 are fixed, and both ends of the pin member 87 are
In a pair of upper and lower grooves 82i formed in the valve body 82,
Therefore, the collar 92 with the female thread is locked with the valve body shaft.
It will move in a linear direction. Also, the pin member 87
The female threaded collar 92 and the sleeve 83 are
It is designed to work in the direction of the de-axis. In the sleeve 83, a female thread
-92 and the spool 84,
Apply biasing force in the direction to separate in the axial direction of the body
A spring 85 is provided. That is, Spring
, The collar 92 with female screw is always stepping
In the direction of the motor (to the left in FIG. 5).
You. In the following, convenience is used unless otherwise specified.
Above, this direction (left direction in FIG. 5) is simply referred to as “left”
The opposite direction (right direction in FIG. 5) is simply called “right”.
And Therefore, the slot that works with the female threaded collar 92
The arm 83 is also constantly urged leftward. In addition,
Spring 85 keeps spool 84 always to the right
It is of course energized. Here, the rotation of the stepping motor 88
When the rotating member 86 rotates accordingly, the pin member 87
The female threaded collar 92 whose rotation is regulated by the valve body
The sleeve 83 is moved in the axial direction,
The main port 83i moves in the valve body axis direction.
Through the groove 84i to the first port 83j or
Communicate with the second port 83k, and
Upshift control port P2 for hydraulic oil (oil pressure) or
Output to shift-down control port P3
You. Here, the hydraulic oil is a hydraulic oil with a predetermined oil pressure
The same applies to the following. Specifically, for example, when shifting up
Is the rotation angle of the stepping motor 88 corresponding to the pulse.
Rotates forward, and the sleeve 83 moves rightward with this
At this time, the main port 83i is connected via the groove 84i.
And communicates with the first port 83j to connect with the original pressure receiving port P1.
Hydraulic oil is output from the shift-up control port P2
You. In this case, the hydraulic oil of the shift-down control port P3
Is released to the drain passage 99. On the other hand, when shifting down, stepping
The motor 88 reversely rotates at a rotation angle corresponding to the pulse,
Accordingly, the sleeve 83 moves to the left, and the main port 8 moves.
3i communicates with second port 83k via groove 84i
And the hydraulic oil (hydraulic) at the source pressure receiving port P1 shifts down.
Is output from the control port P3. In this case, shift
Hydraulic oil of the up control port P2 is returned to the drain passage 99.
Leased. At the time of such a downshift, three
Is always urged leftward by the spring 85
The stepping motor is
The torque limit of 88 has been reduced and the drive speed limit has been increased.
(Step out is unlikely to occur), and the sleeve 83 quickly moves to the left
As a result, the shift response is improved. Note that
When lifting up, the biasing force of the spring 85 is
Increase the torque load on the
The driving limit speed of the ping motor 88 decreases and the speed changes slightly.
Responsiveness will decrease, but when shifting up,
Since there is no need for responsiveness,
Does not occur. The right end of the spool 84 and the first shaft member 61a
Feedback means 90 is provided between the lower end of the
Have been. The feedback means 90 includes a first shaft portion.
Material 61a, and rotates integrally with the first shaft member 61a.
The precess cam 100 is provided.
100 has an inclined surface 100i. Also,
Rotary shaft 1 provided at a predetermined position of upper housing 55
01, the first arm 102i and the second arm 102j
Installed. Here, the tip of the first arm 102i
The end is engaged with the inclined surface 100i of the precess cam 100,
The tip of the second arm 102j is the right end of the spool 84
Is engaged with the slit 84m formed at the bottom. The basic mechanism of the feedback means 90
Noh is a commonly used means of feedback
The details are omitted because they are the same as
In a similar process, the tilt angle (change) of each of the rollers 45a to 45d is determined.
Speed ratio) at the target tilt angle (target gear ratio)
ing. In other words, the stepping mode
Is only the angle corresponding to the target tilt angle (target gear ratio)
When rotated, the sleeve 83 corresponds to this rotation angle
In the axial direction of the valve body,
a to 79d and 80a to 80d are supplied with hydraulic pressure,
The rollers 45a to 45d tilt to the target tilt angle. On the other hand,
When the rollers 45a to 45d tilt as shown in FIG.
In response, each trunnion 59a-59d and each shaft member 61a-
61d rotates, and the precess cam 100 rotates accordingly.
Move. At this time, the first arm is
The rotating shaft 101 is rotated via the
Further, the second arm 102j is moved by the rotating shaft 101.
The spool 84 is connected to the moving direction of the sleeve 83 through the
The rollers 45a to 45d are moved in the same direction and tilted.
When the angle reaches the target tilt angle, the amount of movement of the spool 84
Is exactly equal to the amount of movement of the sleeve 83.
Port 83i and the first port 83j or the second port
83k is cut off, and the hydraulic chambers 79a to 79d, 8
The supply of hydraulic pressure to 0a to 80d is stopped, and the tilt angle changes.
Stops, and the tilt angle is maintained at the target tilt angle. However, such feedback operation is performed.
When the end of the second arm 102j is
When displacing in the direction away from 4 (ie, rightward)
The spool 84 is moved by the spring 85
It is made to follow the displacement of the second arm 102j. Below, oil
Hydraulic oil (oil pressure) is supplied from the pressure supply source to the gear ratio control valve V
And the hydraulic pressure chambers 79a to 79d,
Hydraulic circuit for supplying hydraulic oil to 80a to 80d
I will tell. As shown in FIG. 6, in such a hydraulic circuit
Indicates that the operating oil in the oil pan 36 is
After the pressure is discharged from the
(Original pressure) and then through the original pressure supply passage 123
And supplied to the source pressure receiving port P1 of the speed ratio control valve V.
It is like. Exit from shift-up control port P2
The energized hydraulic oil flows into the common upshift oil passage 130
Thereafter, the first to fourth branch shift-up oil passages 130a
Through 130d, respectively, with the first lower hydraulic chamber 80a,
The second upper hydraulic chamber 79b, the third lower hydraulic chamber 80c,
4 and is supplied to the upper hydraulic chamber 79d. other
, The operation output from the downshift control port P3
The oil flows into the common shift-down oil passage 131, and thereafter,
Via first to fourth branch shift-down oil passages 131a to 131d
And a first upper hydraulic chamber 79a and a second lower hydraulic chamber, respectively.
80b, a third upper hydraulic chamber 79c, and a fourth lower hydraulic chamber 8
0d. In such a gear ratio control device, the shift gear
6, the sleeve 83 moves rightward in FIG.
The hydraulic oil at the source pressure receiving port P1 is used for downshift control.
This hydraulic oil is output from port P3 and is
Chamber 79a, second lower hydraulic chamber 80b, and third upper hydraulic chamber
79c and the fourth lower hydraulic chamber 80d. What
The gear ratio control valve V in FIG. 6 corresponds to the gear ratio in FIGS.
The left and right positional relationship with the control valve V is shown in reverse. At this time, the first and third trunnions 59
a, 59c are displaced upward, and the second and fourth trunnions
59b and 59d are displaced downward, and the trunnion 5
9a to 59d, the first to fourth rollers 45a
４５45d changes to the deceleration side. At this time, each trunnion 5
Each of the shaft members 61a to 61d rotates according to 9a to 59d.
However, with the rotation of the first shaft member 61a, the precessor
Arm 100 is in contact with the inclined surface 100i.
102i, the rotating shaft 101, and the second arm 102j
The spool 84 is shifted to the original pressure receiving port P1 via the
Turn right until the communication of the down control port P3 is cut off.
Move. In this way, the tilt angle is maintained at the target tilt angle
Is done. Here, the sleeve 83 is moved rightward.
When moving, the sleeve 85 is
Since it is urged rightward, the stepping motor 88
Before the torque load was reduced and the shift response was improved,
As described above. On the other hand, when shifting up, three
6 moves to the left in FIG.
1 is output from the shift-up control port P2.
This hydraulic oil is supplied to the first lower hydraulic chamber 80a and the second upper hydraulic chamber 80a.
Hydraulic chamber 79b, third lower hydraulic chamber 80c, and fourth upper oil
The pressure is supplied to the pressure chamber 79d. At this time, the first and third trunnions 59
a, 59c are displaced downward, and the second and fourth trunnions
59b and 59d are displaced upward, and the trunnion 5
9a to 59d, the first to fourth rollers 45a
45d changes to the speed increasing side (overdrive side).
At this time, each of the trunnions 59a to 59d (each of the shaft members 61a
To 61d) rotate, and with the rotation of the first shaft member 61a.
The precess cam 100 comes into contact with the inclined surface 100i.
First arm 102i, rotating shaft 101, and second arm 102i.
102j is activated, in which case the system
Unlike the case of the downshift, the tip of the second arm 102j
The direction in which the end is separated from the spool 84 (leftward in FIG. 6)
). Therefore, the urging force of the spring 85
Therefore, the spool 84 is moved to the left in FIG.
The main pressure receiving port P1 and the shift-up control port P
It is moved to the left until the communication of 2 is cut off. this
Thus, the tilt angle is maintained at the target tilt angle. Next, the book
Shelf pressure of hydraulic clutch 150 which is a characteristic part of the embodiment.
Of the shelf pressure control hydraulic system for controlling the
You. As already described in the section of the prior art,
For clutches, connect the clutch smoothly to
To start both cars smoothly, go through the half-clutch state.
Full connection must be made. for that reason
Is the clutch oil pressure, which is the pressing pressure of the starting clutch.
It is necessary that the time waveform shown in FIG. That is,
The clutch oil pressure changes from zero to half-clutch.
Rise to the pressure required for complete connection via the shelf pressure
Have to change. Also semi-clutch shaped
The shelf pressure in the state is, as shown in FIG.
Must be set high. Control oil pressure for generating such a shelf pressure
FIG. 7 shows the system. In FIG.
In order to explain the principle of the shelf pressure control of the
Rollers 45a to 45d, first to fourth upper hydraulic chambers 79a
To 79d and the first to fourth lower hydraulic chambers 80a to 80d.
In the following description, power is used for convenience.
The force to move the rollers 45a to 45d upward is
The hydraulic chamber to be generated, that is, the first to fourth upper hydraulic chambers 79
a to 79d are represented by PH, and the power roller 4
5a to 45d generate a force to move down
Hydraulic chambers, that is, first to fourth lower hydraulic chambers 80a to 80
The hydraulic pressure generated at d is represented by PL. Also, input data
Disks 43f and 43r, power rollers 45a to 45d and
And output disks 44f, 44r are indicated by arrows A, B, C in the figure.
It shall rotate in the direction shown. The toroidal type schematically represented as described above
In the continuously variable transmission C, the first to fourth power rollers 45
a to 45d are indicated by white arrows as the reaction force of the transmission torque.
A force F proportional to the transmission torque acts in the direction. That
Therefore, upshift control of the three-layer valve V (speed ratio control valve V)
Port P2 and the shift-down control port P3
Hydraulic oil pressure PH output from one side and upshift
Of the control port P2 and the shift-down control port P3
The pressure PL of the hydraulic oil output from the other
Balance with the force F acting on the rollers 45a-45d,
A force is generated to hold the rollers 45a to 45d at predetermined positions.
Differential pressure δP = (PH−PL) is always generated
Will be. Since the force F is proportional to the transmission torque, the difference
The pressure δP is also proportional to the transmission torque.
By inputting to the clutch pressure control valve, the clutch
Can be controlled to a value proportional to the transmission torque.
That is. Next, the configuration of the control hydraulic system shown in FIG.
Will be described. In FIG. 7, the operation in the oil pan 36 is performed.
After the oil is discharged from the oil pump 152,
(Reducing valve) 154 and a predetermined
The pressure is reduced to the duusing pressure. Reduce to reducing pressure
The hydraulic fluid is input to the linear solenoid valve 156.
In the linear solenoid valve 156, the solenoid
By changing the duty ratio, the pressure regulating valve
The pilot valve for controlling the operation of the
To generate pressure. On the other hand, the pressure regulating valve 158 has oil
If the hydraulic oil output from the pump 152 is directly input,
This hydraulic oil is supplied from the linear solenoid valve 156
The pressure is adjusted by the pilot pressure, and the pressure is
Output as in pressure. Adjusted to the specified line pressure
Hydraulic oil is input to the three-layer valve V (speed ratio control valve V),
For upshifting of the three-layer valve V by the control described in
Control port P2 or shift down control port P3
Are output as pressures PH and PL. These hydraulic pressures PH
, PL = δP = (PH−PL) is the power roller 4
5a to 45d act as pressure to move up and down. On the other hand, the hydraulic oil having the pressures PH and PL is as follows:
This is input to the clutch pressure control valve 160. In addition,
The line pressure is input to the
This line pressure is applied by the clutch pressure control valve 160.
And the pressure difference δP between the pressures PH and PL is proportional to (PH-PL).
Is adjusted to the predetermined pressure and input to the starting clutch 150.
You. As a result, the shelf pressure of the starting clutch 150 becomes the differential pressure δ
Pressure proportional to P, ie, toroidal type continuously variable transmission C
Is controlled to a pressure proportional to the transmission torque of the motor. Next, FIGS. 8 and 9 show the clutch pressure control valve.
FIG. 4 is a side sectional view showing a specific configuration of a bush 160. FIG.
In FIG. 9, the clutch pressure control valve 160
Valve body constituting the main body of latch pressure control valve 160
Reciprocate in the axial direction of the valve body 162
The spool 164 is fitted so that it can move.
You. Then, the spool 164 is connected to the compression spring 16 with a weak force.
6 is always urged rightward in the figure. FIG.
Pool 164 moved to the right end of valve body 162
FIG. 9 shows that the spool 164 is a valve body.
162 has been moved to the left end. Where
The line pressure (source pressure) is received by the lube body 162.
Pressure receiving port P4 and pressure from three-layer valve V
1st working pressure receiving port for receiving working fluid of PH
Accepts P5 and hydraulic fluid at pressure PL from three-layer valve V
Operating pressure receiving port P6 and line pressure for starting
A clutch pressure control port P7 for leading to the switch 150;
The feedback pressure (F /
Feedback port P8 for recirculating pressure (B pressure);
Unless torque is applied to the toroidal type continuously variable transmission C
Drain port P9 for releasing clutch pressure
I have. The spool 164 has the structure shown in FIG.
The spool 164 is located at the right end of the valve body 162 in the drawing.
The first to close the line pressure receiving port P4 when it moves
The land portion 164a and the spool 164 as shown in FIG.
Moves to the left end of the valve body 162 in the drawing.
The second land portion 164b for closing the port P9 is formed.
Have been. In addition, the first land portion 164a and the second land
Between the parts 164b through the line pressure receiving port P4
Hydraulic fluid to the clutch pressure control port P7
Annular groove 164c is formed. The first working pressure receiving port P5 and the second
The dynamic pressure receiving port P6 and the feedback port P8
Orifices 167, 168, 170 are attached respectively
And cuts the high frequency component of the hydraulic pressure
Only the components are introduced into the valve body 162.
ing. Next, the clutch pressure control valve configured as described above is used.
The operation of the switch will be described. First, the driver leaves the vehicle
Depressing the accelerator pedal to advance the engine torque
, That is, the input torque of the toroidal type continuously variable transmission C is
To rise. Then, the power rollers 45a to 45d are supported.
The control hydraulic pressures PH and PL to be held vary. Shown in FIG.
When the power rollers 45a to 45d are
Since the force F acting in the downward direction acts, this force F is supported.
Therefore, the control oil pressure PH needs to be higher than PL.
is there. When the control oil pressure PH becomes higher than the oil pressure PL,
In the switch pressure control valve 160, as shown in FIG.
The valve 164 is located at the right end of the valve body 162
Then, the spool 164 is pushed by the hydraulic pressure PH to the left in the drawing.
Move and the line pressure receiving port P4 is gradually opened.
And Receives the hydraulic pressures PH and PL of the spool 164, respectively.
The receiving areas of the
The opening of the pressure receiving port P4 is the difference between the control oil pressures PH and PL.
Pressure .delta.P = proportional to the magnitude of (PH-PL).
Into the groove 164c from the line pressure receiving port P4.
The inflowing hydraulic oil is adjusted to a pressure proportional to the differential pressure δP.
From clutch pressure control port P7 to starting clutch 150
Is introduced. At this time, the feedback port P8
, Through the orifice 168, the clutch pressure
Since the fluid is returned into the body 162, the orifice 168
The hydraulic pressure from which higher frequency components have been removed
Back pressure causes the operation of spool 164 to stabilize,
The opening amount of the pressure receiving port P4 is accurately controlled. Differential pressure
δP is the toroidal type continuously variable transmission C as described above.
Is proportional to the input torque of the starting clutch.
The pressure of the hydraulic oil introduced at 150 is proportional to the input torque
The starting clutch shelf pressure is the magnitude of the input torque.
Will be set to a value proportional to. The value of the differential pressure δP is set as shown in FIG.
Even if the force torque is the same, if the gear ratio changes,
Low side where changes and high torque are required (deceleration side)
Over, where torque is not needed much
It becomes lower on the drive side (speed increasing side). Therefore, this embodiment
According to the magnitude of the input torque
Not only the clutch pressure obtained, but also the gear ratio
Clutch pressure is obtained. In particular, in this embodiment,
The starting clutch 15 is connected to the output side of the toroidal type continuously variable transmission C.
0 is provided, so that the speed change by the transmission C is first performed.
The clutch of the starting clutch 150 at the subsequent stage according to the speed ratio
Since the shelf pressure is controlled, there is no contradiction between the input torque and the gear ratio.
Clutch shelf pressures corresponding to both are obtained. The present invention does not depart from its gist.
It is applicable to a modified or modified version of the above embodiment.
is there. For example, in the above embodiment,
Although an example in which the present invention is applied to a starting clutch is described, the present invention
Is not limited to this,
62-251559
Applicable to control of reverse or reverse clutch
It is. As described above, the toroidal of the present invention
According to the type continuously variable transmission, the following effects can be obtained. You
That is, the power roller outputs the rotational force of the input disk.
The force acting on these discs
Force to move power roller in tangential direction of disc
Works. This force is proportional to the transmission torque. That
The two oils of the hydraulic mechanism that moves and drives the power roller
In the pressure chamber, to generate a force that balances this reaction force
Is generated, and this differential pressure is proportional to the transmission torque.
Become. Therefore, the clutch pressure is controlled using this differential pressure.
If the control pressure of the control valve is adjusted, complicated
Originally without using a near solenoid valve
Transmission using the necessary hydraulic mechanism for driving the power roller
The clutch control pressure proportional to the torque can be obtained.
You.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a cross-sectional view showing a configuration of a toroidal type continuously variable transmission according to an embodiment. FIG. 2 is a side sectional view of the toroidal-type continuously variable transmission shown in FIG. FIG. 3 is a sectional view of the toroidal type continuously variable transmission shown in FIG. 2 taken along line AA. 4 is a sectional view of the toroidal type continuously variable transmission shown in FIG. 2 taken along line BB. FIG. 5 is a side sectional view of a three-layered speed ratio control valve having a sleeve. FIG. 6 is a diagram illustrating a hydraulic circuit of a hydraulic mechanism of the toroidal type continuously variable transmission according to the embodiment. FIG. 7 is a diagram showing a control hydraulic system for generating a shelf pressure of a starting clutch. FIG. 8 is a side sectional view showing a specific configuration of a clutch pressure control valve. FIG. 9 is a side sectional view showing a specific configuration of a clutch pressure control valve. FIG. 10 is a diagram showing a relationship between a differential pressure of a hydraulic mechanism that drives a power roller and an input torque. FIG. 11 is a diagram showing a relationship between clutch pressure and time when the vehicle is started. FIG. 12 is a diagram showing a relationship between a clutch shelf pressure and an input torque. FIG. 13 is a diagram showing a conventional clutch shelf pressure control mechanism. [Description of Signs] C Toroidal type continuously variable transmission V Gear ratio control valve P1 Main pressure receiving port P2 Shift up control port P3 Shift down control port 17 Oil pump 82 Valve body 83 Sleeve 84 Spool 85 Spring 88 Stepping motor 90 Feedback means 150 Starting clutch 162 Valve body 164 Spool 166 Compression spring 167, 168, 170 Orifice

──────────────────────────────────────────────────続 き Continuing on the front page (51) Int.Cl. ⁷ Identification code FI F16D 25/14 640U (72) Inventor Terauchi Politics 3-1, Fuchu-cho Shinchi, Aki-gun, Hiroshima Mazda Co., Ltd. (56) Reference Reference JP-A-6-265001 (JP, A) Japanese Utility Model 62-121460 (JP, U) (58) Fields investigated (Int. Cl. ⁷ , DB name) F16D 48/02 B60K 41/00 301 B60K 41 / 22 F16H 61/00

Claims (1)

(57) [Claim 1] A cone-shaped input disk to which power is input, a cone-shaped output disk arranged coaxially with the input disk and outputting power to the outside, The input disk and the output disk are disposed between opposing cone surfaces, and rotate while contacting both the cone surface of the input disk and the cone surface of the output disk to output the rotational force of the input disk to the output disk. A power roller for transmitting to the disk, and a hydraulic pressure for moving the power roller in a direction substantially perpendicular to the rotation axis of the output disk in order to tilt the power roller to change the speed ratio between the input disk and the output disk. And a starting clutch connected to the output disk side, wherein the hydraulic mechanism uses a differential pressure between two hydraulic chambers provided in the hydraulic mechanism. In serial toroidal type continuously variable transmission has been made as to generate a driving force for moving the power roller, depending on the pilot pressure generated by the solenoid valve
Discharge from oil pump by pressure control valve
The output hydraulic fluid is regulated to generate a line pressure,
And a hydraulic mechanism for moving the power roller.
Pressure control for controlling the clutch pressure of the forward clutch
Control valve and the clutch
Guide the hydraulic pressures of the two hydraulic chambers to a pressure control valve,
The clutch pressure control is performed by using a pressure difference between the two hydraulic chambers.
A toroidal-type continuously variable transmission, wherein a control pressure of a control valve is adjusted .