JPS63258286A - Controller for non-stage transmission - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

Detailed Description of the Invention "Field of Industrial Application" The present invention relates to a continuously variable transmission used in a power transmission system of a motorcycle, etc., and more specifically, to hydraulically adjusting groove width on a drive shaft and a driven shaft. An endless belt is wound between these pulleys, and by adjusting the oil pressure, the groove width of both pulleys is adjusted to change the gear ratio between the driving shaft and the driven shaft. The present invention relates to a control device for a continuously variable transmission that increases/decreases side pressure applied to a continuously variable transmission.

``Prior Art'' The applicant previously proposed one of the control devices for a continuously variable transmission of this type in Japanese Patent Application No. 47374/1983.

This control device includes a hydraulic setting section that sets two types of hydraulic pressure, high pressure and low pressure, to adjust the groove width of both pulleys on the drive side and driven side, and a hydraulic pressure setting section that selectively applies the hydraulic pressure set by this hydraulic pressure setting section to the pulley. The oil pressure setting section sets the oil pressure from the oil pressure generation source to two types of oil pressure, high pressure and low pressure, with a certain difference value, and also sets the oil pressure from the oil pressure generation source to two types of oil pressure, high pressure and low pressure, and is configured to be increased or decreased according to the gear ratio of the continuously variable transmission while maintaining the difference value. In this case, the gear ratio of the continuously variable transmission is detected by the ratio detection section, and the detected value is manually input as an operation signal to the hydraulic pressure increase/decrease operation section of the hydraulic pressure setting section, thereby controlling the overall hydraulic pressure increase/decrease. I have to.

Further, the switching valve switches the oil passage arranged between the oil pressure setting section and the pulley, and supplies appropriate oil pressure to the pulley depending on the speed change state. In other words, the groove width of both pulleys changes depending on the balance of the supplied hydraulic pressure, and the effective diameter changes.The switching valve controls the oil passage to supply low-pressure oil to the pulley that widens the groove width. control to switch the oil passage to supply high-pressure oil to the pulley that reduces the groove width. And with this, the 114 of the pulley
The belt width is adjusted, the belt's effective winding diameter is changed, and the gear ratio changes.

[Problems to be Solved by the Invention] According to such a control device, the set oil pressure increases or decreases depending on the speed ratio, so a side pressure corresponding to the increase or decrease in the oil pressure is applied to the belt. However, the actually required side pressure not only changes depending on the gear ratio as shown in Figure 4, but also changes depending on the torque generated between the input side and the load side as shown in Figure 3. It also changes due to fluctuations in Therefore, the conventional method of controlling the side pressure using only the gear ratio has a problem in that it cannot appropriately respond to torque fluctuations.

Actually, in order to prevent slippage, lateral pressure is applied based on a high torque value, so when the torque is low, an excessive lateral pressure greater than the required lateral pressure is applied to the belt. Therefore, in conventional equipment,
Because excessive frictional force and tension are applied to the belt in response to lateral pressure, it was necessary to improve the strength of the belt. In addition, the application of excessive side pressure resulted in a reduction in power efficiency.

"Means for Solving the Problems" In order to solve the above problems, the present invention provides a power transmission system that newly includes a continuously variable transmission, in addition to a ratio detection section that detects the gear ratio of the continuously variable transmission. The present invention is characterized in that a torque detection section is provided to detect the torque generated in the hydraulic pressure setting section, and the detection value of the ratio detection section and the detection value of the torque detection section are manually operated in parallel as operation signals for the oil pressure increase/decrease operation section of the oil pressure setting section.

"Function" Two signals from the ratio detection section and the torque detection section are manually inputted in parallel to the oil pressure increase/decrease operation section of the oil pressure setting section, so the operation section outputs oil pressure that reflects these two detected values. do. Therefore, an appropriate side pressure can be applied to the belt in accordance with the speed ratio and the torque.

"Example" Hereinafter, one embodiment of the present invention will be described with reference to the drawings.

In FIG. 1, the symbol l is a casing, 2 is a crankshaft rotatably supported by the casing, 3 is a continuously variable transmission, and 4 is a clutch interposed between the continuously variable transmission 3 and the crankshaft 2. show. The continuously variable transmission 3 is controlled by the control device 5 to change gears as appropriate based on a displacement value that is a reference for changing the gear ratio, such as the difference between the ideal engine speed determined by the throttle opening and the actual engine speed. controlled to have a ratio.

The rotation of the crankshaft 2 is transmitted to the clutch 4 via a gear 6 attached to the crankshaft 2 and a clutch-side gear 7 meshed with the gear 6.

The clutch 4 is disposed on the input shaft IO of the continuously variable transmission 3, and includes a rotating body 1 rotatably arranged with respect to the input shaft IO.
1 (the gear 7 is integrally formed on the outer periphery of the rotating body 11), a rubber inner 13 attached to the rotating body 11 via a damper mechanism 12, and an input horn shaft 1.
Clutch outer 14 is attached to rotate integrally with respect to clutch outer 14, friction plates 15a and 15b are interposed between clutch inner 13 and clutch outer 14, and clutch outer 14 rotates integrally with clutch outer 14. Yonikatsu A, B
It consists of a clutch piston 16 that is provided so as to be movable in one direction and a centrifugal governor mechanism 17 that is interposed between the boss portion 11a of the rotating body 11 and the clutch inner 13.

The clutch 4 having the above configuration is constructed by the introduction boat 1 of the casing 1.
Feed pipe 18 arranged at the axial center of the input shaft 10 from b
When pressure oil is introduced into the pressure oil flow path 19 inside the input shaft IO through the pressure oil flow path 19, the pressure oil is introduced into the through hole IQa provided in the input shaft 10 in the radial direction and the pressure connected thereto. Although the oil is guided through the oil passage 20 to the pressure chamber 21 formed on the right side of the clutch piston 16 in the figure,
When the rotation is less than a predetermined rotation (for example, rotation during idling), the centrifugal governor mechanism 17 disposed in the pressure oil flow path 20
The flow path control pin 22 associated with is in a position not shown in the figure,
Since the pressure oil applied to the pressure chamber 21 escapes to the outside from the hollow part of the flow path control pin 22 and the opening 22a extending in the radial direction, the pressure in the pressure chamber 21 does not reach a predetermined pressure, and the clutch 4 is not in the connected state. No.

When the rotation of the human power shaft 10 exceeds a predetermined rotation, the ball 23 of the centrifugal governor mechanism 17 moves outward due to centrifugal force, moves the moving member 25 in the direction B against the spring 24, and The control pin 22 is moved in the same direction. As a result, the opening 22a of the pin 22 is closed,
All of the pressure oil introduced into the pressure oil flow path 19 in the input shaft IO is guided to the pressure chamber 21 to create an internal pressure in the pressure chamber 21, and moves the clutch piston 16 in six directions, causing the friction plates 15a, 15
Press b strongly against each other. As a result, the rotation of the rotating body 11 connected to the crankshaft 2 is controlled by the clutch inch 13.
, both friction plates +5aS 15b, and the clutch outer 14 to be transmitted to the input shaft 10, that is, the clutch is connected.

The continuously variable transmission 3 has a manpower shaft 10 and an output shaft 26 rotatably provided in the casing l, a drive pulley 27 is attached to the input shaft IO so as to rotate integrally with the manpower shaft 10, and , the drive pulley 2 is attached to the output shaft 26.
The basic configuration is such that a driven pulley 28 paired with 7 is attached to rotate integrally with the output shaft 26, and an endless belt 29 is wound between the driving pulley 27 and the driven pulley 28.

The drive pulley 27 includes a fixed pulley half 27A formed integrally with the input shaft IO on the side of the input shaft 10 facing the clutch 4, and a fixed pulley half 27A formed on the input shaft 10 opposite to the fixed pulley half 27A. It consists of a movable pulley half 27B fitted to the outer periphery via balls 30 so as to be movable in the axial direction and non-rotatable relative to each other. A boss portion 32 and a cylindrical portion 33 outside the boss portion 32 are integrally formed on the opposite side of the movable pulley half 27B from the fixed pulley half 27A. A piston member 34 is provided between the boss portion 32 and the cylindrical portion 33 so as to be immovable in the axial direction with respect to the human power shaft 10 and to rotate together with the piston member 34 and the movable pulley half 31. A pressure chamber 35 is formed between the two.

In the driving pulley 27, when pressure oil is introduced from the introduction port Ia into the flow path 36 arranged on the outside of the feed pipe 18 located at the axis of the input shaft IO, the introduced pressure oil is transferred to the input shaft 10. a radially extending through hole 37 formed in the
The oil is guided to the pressure chamber 35 through the oil passage formed between the boss portion 33 and the piston member 34 and increases the pressure in the same chamber 35, thereby moving the movable pulley half 27B in six directions and increasing the pressure of the pulley 27. Try to narrow the groove width.

On the other hand, the driven pulley 28 also has substantially the same configuration as the drive pulley 27 described above. That is, the driven pulley 28 includes a fixed pulley half 28A integrally formed on the outlet J side 26, and a ball on the outer periphery of the output shaft 26 that is movable in the axial direction with respect to the output shaft but cannot rotate relative to the output shaft. 39
It consists of a movable pulley half 28B fitted via...

A boss portion 41 and a cylindrical portion 42 on the outside thereof are integrally formed on the movable pulley half 28B. Piston member 4 provided to rotate integrally
3 is fitted, and a pressure chamber 44 is formed between the piston member 43 and the movable pulley half-rest 40.

In the driven pulley 28, when pressure oil is introduced from the introduction boat lc into the pressure oil passage 46 inside the output shaft 26 via the feed vibe 45 arranged at the axial center of the output shaft 26, the introduced pressure is The oil flows through a through hole 47 extending in the radial direction of the output shaft 26.
The movable pulley half 28B is moved in the direction B to narrow the groove width of the pulley 28.

Further, when pressure oil is introduced into the introduction boat Id formed in the casing 1, the introduced pressure oil flows toward the flow path 48 formed outside the feed vibe 45 of the output shaft 26 and in the radial direction of the output shaft 26. It is guided to the outer periphery of the output shaft 26 through the extending through hole 49, and further reaches the outer endless belt 29 by receiving centrifugal force from there, and lubricates the endless belt 29.

In the continuously variable transmission 3 configured as described above, the rotation of the input shaft 10 can be transmitted to the output shaft 26 via both pulleys 27 and 28 and the endless belt 29 wound between them, and furthermore, By introducing low and high pressure oil into the pressure chamber 35.44 attached to the driven pulley 28,
The movable pulley halves 27B and 28B are moved in directions A and B, and the groove widths of both pulleys 27 and 28 are changed to transmit the rotation of the input shaft 10 to the output shaft 26 at an arbitrary gear ratio. Can be done.

In the illustrated continuously variable transmission 3, a spring 50 is disposed between the piston member 43 of the driven pulley 28 and the movable pulley half 28B. When pressure oil is no longer introduced into the chambers 35 and 44, an appropriate tension is applied to the endless belt 29, and the movable pulley half 28B is moved in the direction B by the biasing force of the spring 50, and a small torque is generated when restarting. This is for changing the gear ratio to a desired speed ratio that allows the output shaft 26 to be rotated. A sprocket (not shown) is attached to one end of the output shaft 26, and the output shaft 26 is
rotation is transmitted to the drive wheels.

On the other hand, the control device 5 includes a pump 51 which is a pressure oil supply source.
and pressure oil connection boats Ia to ld integrally provided in the casing l housing the continuously variable transmission 3, and the pressure oil supplied from the pump 51 is controlled to a certain difference value. The low and high pressure setting section (hydraulic setting section) divides the low and high pressure pressure oil thus divided into low and high pressure, and changes the overall pressure according to the gear ratio of the continuously variable transmission 3 while maintaining a constant difference value. Department)
52, and a switching valve 53 that selectively guides the low/high pressure oil set by the low/high pressure setting section 52 to the pressure chambers 35, 44 attached to the driving and driven pulleys 27, 28. It is equipped with Note that 54 is a clutch switching valve for switching the clutch 4 on and off.

The low/high pressure setting section 52 includes a fixed cylinder 55, a differential pressure regulator piston 56 fitted into the fixed cylinder 55 so as to be slidable in directions A and B, and an ASB on the outer periphery of a small diameter section 55a on the right side in the figure of the cylinder 55. A movable sleeve 57 fitted so as to be slidable in directions, and a ratio interlocking regulator piston 5 fitted into the movable sleeve 57 so as to be slidable in directions A and B.
8.

The differential pressure regulator piston 56 is urged in the inward direction by a differential pressure regulator spring 59 whose one end is supported by a snap ring attached to the inner periphery of the fixed cylinder 55.
8 is biased in the inward direction by a ratio interlocking regulator spring 60 whose one end is supported on the casing side. Further, a ratio pickup lever 61 for detecting the speed ratio is formed on the movable sleeve 57 and extends outward, and the tip of the ratio pickup lever 61 is connected to the movable pulley half of the drive pulley 27 of the continuously variable transmission 3. 27B
The movable sleeve 57 is engaged with the groove 27x of the movable pulley half 27B, so that the movable sleeve 57 moves in the directions A and B integrally with the movable pulley half 27B.

An introduction boat 62 is installed at a predetermined location on the outer circumference of the fixed cylinder 55.
Outlet boats 63 and 64 are provided, and the inlet boat 62 is connected to the pump 51 via a pressure oil passage 65. Additionally, a drain boat 6 is provided on the outer periphery of the movable sleeve 59.
6 is provided, and the drain boat 66 is connected to a tank 68 via an oil passage 67.

The fixed cylinder 55 has radially extending through holes 69,70.
．． 71 are provided at predetermined intervals in the axial direction. The through hole 69 is for communicating the pressure chamber 72 formed in the cylinder 55 on the left side of the differential pressure regular piston 56 with the introduction boat 62 and the outlet boat 63, respectively. It is opened and closed by the movement of the pressure regular piston 56, and when opened, the pressure chamber 72 is communicated with a space 73 connected to the outlet boat 64 formed outside the cylinder 55. 'Otsu' and also through hole 7
Reference numeral 1 designates an opening for communicating the space 73 with a space 74 formed within the cylinder 55 and on the right side of the differential pressure regulator piston 56.

Further, a through hole 75 extending in the radial direction is provided at a predetermined location of the movable sleeve 57. This through hole 75 is opened and closed as the ratio interlocking regulator piston 58 moves, and when opened, the movable sleeve 5
The space 76 connected to the drain port 66 formed on the outer periphery of the drain port 7 is connected to the drain port 66 .

In the low/high pressure setting section 52 , pressure oil supplied from the pump 51 via the pressure oil passage 65 is guided from the introduction boat 62 to a space 72 formed on the left side of the differential pressure regulator piston 56 . When the pressure within this space 72 becomes higher than a predetermined pressure, the piston 56 moves to the differential pressure regulator spring 59.
The cylinder 55 moves in the direction B to open the through hole 7.0 formed integrally with the cylinder 55, and the space 7 is opened through the through hole 70.
A space 73 formed outside the cylinder 55 transfers the pressure oil inside the cylinder 55.
to escape. In other words, the pressure PI in the space 72 is equal to the pressure PI in the space 73.
The pressure P of 74 becomes higher by the biasing force of the differential pressure regulator spring 59.

On the other hand, when the pressure P in the spaces 73 and 74 becomes higher than the predetermined pressure, the ratio interlocking regulator piston 58 moves in the direction B against the ratio interlocking regulator spring 60, and the through hole 75 formed in the movable sleeve 57 moves. Open the
The pressure oil in the space 73 is returned from the drain boat 66 to the tank 68 side via the oil passage 67.

Further, the movable sleeve 57 is connected to the drive pulley 27 which is engaged via the ratio pickup lever 6I as described above.
The movable pulley half-rest 27B moves in the ASB direction, and the position of the through hole 75 varies depending on the position of the movable sleeve 57. Therefore, space 73
．． The pressure P2 of 74 is determined by the biasing force of the regulator interlocking spring 60 and the position of the movable sleeve 57.

That is, in the low/high pressure setting section 52, high pressure oil is led out from the lead-out boat 63 connected to the space 72, and low-pressure oil is led out from the lead-out boat 64 connected to the space 73. As shown in FIG. 2, the extracted pressure oil maintains a constant differential value determined by the differential pressure regulator spring 59.
As the groove width of the drive pulley 27 becomes wider, the movable sleeve 57 moves in the B direction, so the overall pressure increases.
Conversely, the narrower the groove width of the drive pulley 27, the lower the overall pressure.

In this way, in the low/high pressure setting section 52, the overall oil pressure increases or decreases depending on the width of the groove of the drive pulley 27, that is, the speed ratio.

In this case, the lever 61 and the groove 27x of the drive pulley 27 that engages with the lever 61 function as a ratio detection section.

Furthermore, the low/high pressure setting section 52 is configured such that its overall oil pressure increases/decreases even with fluctuations in torque.

That is, a rod 77 is connected to the rear surface of the ratio interlocking regulator piston 58.
A torque interlocking piston 78 is provided at the rear end of the piston 78 .

This piston 78 is a cylinder 7 fixed to the casing.
It is slidably housed inside the seven cylinders and can slide in directions A and B depending on the magnitude of the hydraulic pressure introduced into the hydraulic chambers 80 in the seven cylinders.

Therefore, a force directed in the input direction corresponding to the pressure P3 in the hydraulic chamber 79 acts on the regulator piston 58 in conjunction with the biasing force of the regulator spring 60. Therefore, the higher the oil pressure [1]3 becomes, the greater the force that pushes the Lenault interlocking regulator piston 58 in the input direction, and as a result, the pressures P2, P become higher. Furthermore, as the oil pressure P becomes smaller, the force that pushes the reno interlocking regulator piston 58 in the inward direction becomes weaker, and as a result, the pressures P t and P 3 become lower.

In this case, the pressure P3 is determined by the continuously variable transmission 3, as described later.
It is designed to be proportional to the magnitude of the torque generated within the power transmission system including the Therefore, the overall oil pressure set by the low/high pressure setting section 52 is proportional to the magnitude of the torque; the larger the torque, the higher the oil pressure, and the smaller the torque, the lower the oil pressure.

By the way, in the upper low/high pressure setting section 52, the lever 6
The input of the speed ratio detection value by the operation 1 and the manual input of the torque detection value by the hydraulic pressure P are performed at the same time. However, since both are manually operated in parallel and are in an independent relationship, the output oil pressure has a value that reflects both inputs, that is, the speed ratio and torque, respectively.

Next, the torque detection system will be described. The torque detection system is a torque detection section 90 that actually mechanically detects torque.
and a torque valve 100 that converts the mechanical detection signal detected by the torque detection section into a hydraulic signal.

The torque detection unit 90 connects the gear 6 attached to the crankshaft 2, the damper cam 91 attached to the end of the crankshaft 2 so as to be slidable in the axial direction but not rotatable, and the damper cam 9I to the gear 6. It is a grooved structure that combines a damper spring 92 that presses against the damper cam 91 and a pickup lever 93 that engages with the damper cam 91.

The gear 6 in this case meshes with the gear 7 on the clutch 4 side, is rotatably attached to the crankshaft 2, and is pressed against the stepped portion 2a of the crankshaft 2. This gear 6
There are two recesses 6a at target positions on the same circumference on the outer surface of the
is formed.

As shown in FIG. 2, these four parts 6a are inclined so that they are deep in the center and become shallower toward the ends in the circumferential direction.
The cross section is approximately isosceles triangular. 6b is a protrusion for preventing popping out.

One damper cam 91 has a cylindrical shape, and is mounted on the crankshaft 2 with two cam parts 91a protruding toward the gear 6 inserted into a recess q6a on the side surface of the gear 6. ing. The damper cam 91 is urged in the inward direction by the damper spring 92, and presses the cam portion 91a at the tip against the bottom surface of the gear recess 6a.

Note that the damper spring 92 is interposed between the rear end of the damper cam 91 and a spring receiver 94 fixed to the end of the crankshaft 2.

With this configuration, the cam portion 9La of the damper cam 91 rides on the slope of the recess 6a of the gear 6 in response to the torsional moment, that is, the torque acting between the crankshaft 2 and the gear 6, and thereby the damper cam 91 The damper spring 92 is displaced axially outward, that is, in the B direction, against the biasing force of the damper spring 92. This amount of displacement is proportional to the torque, and this amount of displacement is taken out as a torque detection value by the pickup lever 93 that engages with the groove 91b of the damper cam 91. In this case, power from the crankshaft 2 is transmitted to the gear 6 via the damper cam 91.

Further, the torque valve 100 includes a fixed cylinder 101,
A fixed piston 102 provided at one end inside the fixed cylinder lot, a movable sleeve 103 provided slidably in directions A and B between the inner periphery of the fixed cylinder 101 and the outer periphery of the fixed piston 102, and the movable sleeve 103. A inside
, a regulator piston 104 inserted so as to be slidable in the B direction, and a regulator spring 105 that biases the regulator piston 104 in the A direction.A torque pickup lever 93 is attached to one end of the movable sleeve 103. The movable sleeve 103 is integrally formed with the damper cam 91 and moves in the ASB direction.

An introduction boat 106 is installed at a predetermined location of the fixed cylinder 101.
, a lead-out boat 107 are provided, and an introduction boat h1
06 is connected to a boat 63 on the high pressure oil supply side of the low/high pressure setting section 52, and an outlet boat 107 is guided to the tank 68 side. On the other hand, the movable sleeve +03 is provided with through holes 108 and 109 passing through it in the radial direction at predetermined intervals in the axial direction.

Further, the regulator piston 104 has a cylindrical shape whose longitudinal center portion is partitioned by a partition wall 104a.
A through hole 110 is formed in the peripheral wall of the cylindrical portion protruding from 4a in the direction A in the figure, and a shallow groove 11 is formed in the outer peripheral surface communicating with the through hole 11O.
1 is formed all around the circumference. The length and width of this shallow groove 111 in the A and B directions are set with high precision in accordance with the interval between the through holes 108 and 109 of the movable sleeve 103,
Due to the positional relationship between the movable sleeve 103 and the regulator piston +04, the groove 111 communicates with only one of the two through holes 108 and +09 of the movable sleeve. When not communicating, the regulator piston 104 closes the through hole 108 or +09 on the movable sleeve 103 side. Note that the openings to the inner surfaces of the cylinders of the boats 106 and 107 are spaces 106a and 10 having predetermined dimensions in the axial direction.
7a, so that when the movable sleeve 103 moves, it always communicates with the through holes 108 and 109.

The switching valve 53 includes a spool 131 provided within the cylinder 130 so as to be movable in directions A and B;
and an operating mechanism 132 that operates the engine according to the throttle opening degree and the rotation status of the ennon.

The cylinder 130 is provided with an introduction boat +33, 134 and an outlet boat 135, 136, one of the introduction boats +33 is connected to the boat 63 on the high pressure oil supply side of the low/high pressure setting section 52 via an oil passage 137, The other introduction boat 66 is connected to the boat 64 on the low-pressure oil supply side of the low-high pressure setting section 52 via an oil passage 138. Further, the lead-out boat 135 is connected to the introduction boat la via a supply path 139, and the other lead-out boat 136 is connected to the introduction boat 1c via a supply path 140.

When the spool 131 is in the position shown in the figure, the lead-out boat 135 is connected to the high-pressure side introduction boat +33 via the ring groove 141 formed on the outer periphery of the spool 131, and the lead-out boat 136 is connected to the spool 13'l It is connected to the introduction boat 133 on the high pressure side via a space 142 formed inside the spool and a ring groove 143 on the outer periphery of the spool, and high pressure oil is led out from both outlet ports +35 and 136. Therefore, at this time, the drive
Pressure oil on the high pressure side is guided to the pressure chambers 35, 44 of the movable pulleys 27, 28 on the driven side, and the groove widths of the driving and driven pulleys 27, 28 do not change.

When the operating mechanism 132 is operated and the spool 131 moves in the incoming direction from the position shown in the figure, the outlet boat 135 is connected to the introduction boat 134 on the low pressure side via a ring groove 144 formed on the outer periphery of the spool 131. The lead-out boat 136 is connected to the high-pressure side introduction boat 133 via a space 142 and a ring groove 143, as in the serious case. Therefore, at this time, the pressure oil on the low pressure side is transferred to the lead-out boat 135,
The pressure 7IIltM is introduced into the pressure chamber 35 associated with the driving pulley 27 via the passage 139, while the pressure oil on the high pressure side is introduced into the pressure chamber 44 of the driven pulley 28 via the outlet boat 136 and the pressure oil passage 1-40. As a result, the groove width of the driving pulley 27 widens, the groove width of the driven pulley 28 narrows, and the gear ratio changes to the deceleration side (low).

On the other hand, when the spool 131 moves from the position shown in the figure in the direction B, the outlet boat 135 is connected to the introduction boat +33 on the high pressure side, and the outlet boat +36 is connected to the introduction boat 134 on the low pressure side, contrary to the above. Then, drive pulley 2
The high pressure side pressure '/II] is introduced into the pressure chamber 35 of the driven pulley 28, and the low pressure side pressure oil is introduced into the pressure chamber 44 of the driven pulley 28, and the groove width of the drive pulley 27 is The groove width of the pinched driven pulley 28 widens, changing the speed ratio in the opposite direction to that described above.

The operating mechanism 132 moves a rod 152 in directions A and B by rotating an arm 151 that is rotatably provided around a fulcrum pin 150, and moves a servo piston 153 (described later) in the same direction using hydraulic pressure. direction to change the urging force acting on the spool 131 of the spring 154 that is in contact with the left side of the servo piston 153, and thereby,
It is structured to move the spool +31 to a desired position.

Rod 152 and servo piston! To explain the movement of 53, for example, when the rod 152 is moved in six directions from the position shown in the figure, the hole 157 extending radially outward from the pressure oil passage 156 in the rod 152 and the servo piston 153 side The pressure oil introduced into the pressure oil flow path 160 through the introduction boat 159 connected to the high pressure flow path 137 flows into the right side space 160 of the servo piston 153. was introduced in
The servo piston 153 is pressed by the pressure oil introduced into the space 160 and moves in the A direction to a position where the holes 158 and 157 are no longer connected, that is, by an amount equal to the amount by which the rod 152 has been moved.

Further, when the rod 152 is moved in the direction B, contrary to the above, the servo piston 153 is moved in the direction B.
moves in the B direction by the amount moved.

When moving the servo piston 153, for example, when moving the servo piston 153 in the A direction, the greater the amount of movement, the greater the biasing force of the spring 154, so a larger force is required to overcome it. However, in the illustrated example, the structure is not one in which the rod 152 directly presses one end of the spring 154, but a structure in which the servo piston 153 is moved by hydraulic pressure and the servo piston 153 presses the end of the spring 154. , a constant force is sufficient to move the rod 152.

A space 142 in the spool 131 of the switching valve 53 is communicated with a space 147 on the left side thereof through an orifice 146, and the space 147 is connected to a pressure oil passage 148 and an introduction boat le.
It is connected to a hydraulic centrifugal governor 180 via.

The centrifugal governor 180 is rotatably installed in a casing l housing the continuously variable transmission 3 via a bearing 181 and connected to an input shaft lO via gears 182 and 183, and a governor shaft 184. A governor house 185 formed integrally, and a C,
A governor weight 186 that is slidably inserted in the D direction;
Piston 1 inserted into the cylinder of governor house 185
87. Governor weight! 86 is fitted onto the end of a rod 188 extending from one end of the piston 187 so as to move integrally with the piston 187. The governor weight 186 is biased in the C direction by a spring 189.

Pressure oil introduced from the pressure oil passage 148 via the boat le is guided to a pressure chamber 191 formed on the back side of the piston 187 via an oil passage 190. When the pressure in the pressure chamber 191 increases, the piston 187 is pushed outward (in the direction D in the figure) against the biasing force of the spring 189 and the centrifugal force acting on the governor weight 18B, and the A hole 192 leading to the outside communicates with the pressure chamber 191, and the pressure oil in the pressure chamber 191 is discharged to the outside.

That is, the pressure P4 in the pressure chamber 191 is determined by the biasing force of the spring I89 and the centrifugal force acting on the governor weight 186, and increases as the rotation of the governor shaft 184 increases.

Namely, this centrifugal governor! By 80, the pressure chamber 19
1 pressure is fed back to the space 147 of the switching valve 53, so that the actual rotation speed of the input shaft IO and the ideal rotation speed of the input shaft 10 according to the throttle opening at that time become equal. The position of the spool 131 can be adjusted automatically.

Next, the clutch switching valve 54 will be explained.

The clutch switching valve 54 is connected to the lead-out boat 2 of the switching valve 53.
10 and the introduction boat tb of the casing 1, the clutch 4 is operated on and off by supplying or cutting off pressure oil to the clutch 4. Pressure oil introduced from the boat 212 via the pressure oil passage 211 is guided to the space 2+4 in the cylinder 213, and from there passes through the space 216 formed inside the piston 215, which is movable in the A and B directions, to the outlet boat 217. From there, the oil is further guided through the pressure oil passage 218 to the introduction boat Ib of the casing I.

When a clutch lever (not shown) is operated to rotate the arm 219 in the E direction, the piston 215 is pushed by the tip of the arm 219 and moves in six directions against the spring 220. The opening 221 located in the opening 221 shifts from the outlet boat 217, cutting off the supply of pressure oil to the introduction boat lb. As a result, the clutch 4 can be placed in a disengaged state.

Conversely, to bring the clutch 4 into the connected state, the piston 215 may be returned to its original position by operating a clutch lever (not shown) and rotating the arm +51 in the opposite direction to that described above.

In the illustrated clutch switching valve 54, if the pressure in the clutch pressure chamber 21 does not exceed a predetermined level, the pressure in the oil passage 214 in the piston 213 increases as well, causing the piston 213 to resist the spring 222. and move in direction A to insert the opening 223 of the piston 213 into the introduction boat 2.
12 to cut off pressure oil from entering from the introduction boat 212.

Therefore, the pressure within the clutch pressure chamber 21 never exceeds a predetermined level.

As described above, according to the above continuously variable transmission 3, when the throttle opening is at a certain value, the gear ratio is adjusted so that the actual engine rotation speed matches the ideal engine rotation speed determined by the throttle opening. can be determined automatically. that time,
A signal corresponding to the gear ratio is input manually to the operating section of the low/high pressure setting section 52 via the movable sleeve 57, and a signal corresponding to the torque is input as a hydraulic signal to the ratio interlocking regulator piston 58. Since the signals are input in parallel, the oil pressure corresponding to both signals will be output as the set oil pressure. Therefore, a side pressure that depends on the gear ratio and torque can be applied to the belt, and a phenomenon in which excessive frictional force or tension is applied to the belt even though the torque is small is eliminated.

Furthermore, in this embodiment, the mechanical output signal from the torque detection section 90 is not directly inputted to the low/high pressure setting section 52;
Since the torque valve 100, which incorporates the regulator piston 104 and the movable sleeve 103, converts it into hydraulic pressure and uses manual force, the operation reaction force hardly acts on the torque pickup lever 93, and the groove between the lever 93 and the damper cam 91 The sliding resistance with respect to 91b can be kept extremely small. Therefore, wear of the sliding portion is prevented, and power loss due to sliding resistance is reduced.

"Effects of the Invention" The present invention provides a torque detection section that newly detects the torque generated in the power transmission system including the continuously variable transmission, in addition to the ratio detection section that detects the gear ratio of the continuously variable transmission. Since the detection value of the ratio detection section and the detection value of the torque detection section are manually operated in parallel as operation signals for the oil pressure increase/decrease operation section of the oil pressure setting section, the oil pressure setting section can set the oil pressure that reflects these two detection values. Output. Therefore, an appropriate side pressure can be applied to the belt in accordance with the speed ratio and the torque.

Therefore, the following effects can be obtained.

■ Appropriate frictional force and tension according to the torque will be applied to the belt, eliminating the need to provide excessive strength to the belt.

■Since oil pressure is set according to torque, power loss is reduced.

[Brief explanation of the drawing]

Fig. 1 is a configuration diagram showing a continuously variable transmission and its control device according to an embodiment of the present invention, Fig. 2 is a sectional view taken in the direction of the ■ arrow in Fig. 1, and Fig. 3 shows the relationship between torque and required side pressure. 4 are diagrams showing the relationship between the required side pressure and the ratio when the torque is constant. ■...Casing, 2...Crankshaft, 3...Continuously variable transmission, 4...Clutch, 5...Control device, IO...Input axis,
26... Output shaft, 27... Drive pulley, 27x... Groove, 28 Old... Driven pulley, 35
...Pressure chamber, 44...Pressure chamber, 51...
...Pump, 52...Low and high pressure setting section, 53...
...Switching valve, 61...Reno pickup lever, 9o...Torque detection section, 91...
・Torque valve.

Claims (1)

[Claims] A pulley whose groove width can be adjusted by hydraulic pressure is provided on each of the driving shaft and the driven shaft, an endless belt is wound between these pulleys, and the groove width of both pulleys is adjusted by adjusting the hydraulic pressure. In a control device for a continuously variable transmission that changes the gear ratio between the drive shaft and the driven shaft, and also increases or decreases the side pressure applied to the belt by adjusting the hydraulic pressure, the hydraulic pressure from the hydraulic pressure source is controlled to have a certain difference value. an oil pressure setting section that sets two types of oil pressure, high pressure and low pressure, and increases or decreases these two types of oil pressure while maintaining the difference value; a switching valve that selectively supplies power to each of the pulleys; a ratio detection section that detects a gear ratio of the continuously variable transmission; and a torque detection section that detects torque generated in a power transmission system including the continuously variable transmission. A control device for a continuously variable transmission, characterized in that a detected value of the ratio detecting section and a detected value of the torque detecting section are inputted in parallel as operation signals to a hydraulic pressure increase/decrease operating section of the hydraulic pressure setting section.