JP2011085175A - Hydraulic control device of belt-type continuously variable transmission - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To avoid the complication of the structure of a hydraulic control device of a belt-type continuous variable transmission in preventing the energy loss of a hydraulic control device which supplies oil to an oil pressure chamber. <P>SOLUTION: The hydraulic control device of the belt-type continuously variable transmission includes a belt 4 wound around a primary pulley 2 and a secondary pulley 3, wherein are provided a first oil pressure chamber 9 for compression for pushing the first movable piece 7 of the primary pulley 2 to the belt 4, a second oil pressure chamber 20 for compression for pushing the second movable piece 15 of the secondary pulley 3 to the belt 4, a third movable piece 22 which contacts with the first movable piece or the second movable piece and is able to move in a direction along the rotation axis line, an oil pressure chamber 25 for speed change for providing a thrust force to the third movable piece 22 to control a gear ratio, and a connection oil path 32 which connects the first oil pressure chamber 9 for compression with the second oil pressure chamber 20 for compression to allow the oil to go back and forth at the time of changing the gear ratio between the first oil pressure chamber 9 for compression and the second oil pressure chamber 20 for compression. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention relates to a hydraulic control device for a belt-type continuously variable transmission configured by winding a belt around a primary pulley and a secondary pulley.

  An example of a hydraulic control device that controls a transmission ratio of a belt-type continuously variable transmission that is configured by winding a belt around a primary pulley and a secondary pulley is described in Patent Document 1. In the hydraulic control device for a belt-type continuously variable transmission described in Patent Document 1, the primary pulley has a fixed sheave and a movable sheave, and the secondary pulley has a fixed sheave and a movable sheave. In addition, a primary oil chamber that generates thrust to be applied to the movable sheave of the primary pulley is provided, and a secondary oil chamber that generates thrust to be applied to the movable sheave of the secondary pulley is provided. Furthermore, a pump driven by a motor is provided, and this pump has two discharge ports. One discharge port is connected to the primary oil chamber, and the other discharge port is connected to the secondary oil chamber. This pump is a reversible pump, and can move the working oil in the primary oil chamber to the secondary oil chamber, thereby downshifting the belt-type continuously variable transmission. On the other hand, the hydraulic oil in the secondary oil chamber can be moved to the primary oil chamber, whereby the belt-type continuously variable transmission can be upshifted.

  On the other hand, a switching valve is connected to the primary oil chamber and the secondary oil chamber. This switching valve is configured to be switchable between the first state and the second state. When the switching valve is switched to the first state, the pressure line to which oil discharged from an oil pump driven by the engine is supplied is connected to the secondary oil chamber, and the pressure line and the primary oil chamber are connected. And are cut off. On the other hand, when the switching valve is switched to the second state, the pressure line and the primary oil chamber are connected, and the pressure line and the secondary oil chamber are shut off. The switching control between the first state and the second state of the switching valve is performed so that the pressure of the hydraulic oil in the pressure line is supplied to the pulley oil chamber having the smaller thrust.

  Note that hydraulic control devices for belt-type continuously variable transmissions are also described in Patent Documents 2 and 3. In the hydraulic control device for a belt-type continuously variable transmission described in Patent Document 3, a first hydraulic chamber and a second hydraulic chamber that provide thrust to the movable piece of the primary pulley are provided, and the secondary pulley A third hydraulic chamber and a fourth hydraulic chamber that provide thrust to the movable piece are provided. Further, the second hydraulic chamber and the fourth hydraulic chamber are connected by an oil passage, and the oil is configured to go back and forth between the second hydraulic chamber and the fourth hydraulic chamber. Further, a flow control valve for supplying oil to the first hydraulic chamber and the second hydraulic chamber and a flow control valve for discharging oil from the first hydraulic chamber and the second hydraulic chamber are separately provided. .

JP 2005-226730 A Japanese Utility Model Publication No. 63-1955 Japanese Patent Laying-Open No. 2005-155897

  In the hydraulic control device for a belt-type continuously variable transmission described in Patent Document 1 above, oil is moved back and forth between the primary oil chamber and the secondary oil chamber at the time of shifting, and the oil is not discharged to the outside. Oil energy loss can be suppressed. However, in the control device for the belt-type continuously variable transmission described in Patent Document 1, a pump and a motor are provided in order to move oil back and forth between the primary oil chamber and the secondary oil chamber. There is a problem that the structure of the hydraulic control device becomes complicated. On the other hand, according to the hydraulic control device described in Patent Document 3, it is configured such that oil flows back and forth between the second hydraulic chamber and the fourth hydraulic chamber without using a pump or a motor. Since both the primary pulley and the secondary pulley have two hydraulic chambers, there is still a problem that the structure of the hydraulic control device becomes complicated.

  It is an object of the present invention to provide a hydraulic control device for a belt-type continuously variable transmission that can avoid a complicated structure in suppressing energy loss of oil supplied to a hydraulic chamber. .

  In order to achieve the above object, the invention of claim 1 includes a primary pulley and a secondary pulley that are rotatably provided, and a belt wound around the primary pulley and the secondary pulley, In the hydraulic control device for a belt-type continuously variable transmission configured to change the gear ratio with the secondary pulley steplessly, the primary pulley is movable in the direction of the rotation center line. There is provided a first clamping pressure hydraulic chamber that has a movable piece and generates a clamping pressure that is supplied with oil and presses the first movable piece against the belt in a direction along the rotation center line.

  According to a first aspect of the present invention, in addition to the above-described configuration, the secondary pulley has a second movable piece that is movable along a rotation center line direction, and is supplied with oil to rotate the second movable piece. A second clamping pressure hydraulic chamber that generates a clamping pressure to be pressed against the belt in the direction along the center line, and the first movable piece or the second movable piece in contact with the first movable piece and movable in the direction along the rotation center line A third movable piece, a transmission hydraulic chamber for controlling the speed ratio by supplying oil to the third movable piece in a direction along the rotation center line, and the first sandwiching piece. The pressure hydraulic chamber and the second clamping hydraulic chamber are connected, and oil is passed back and forth between the first clamping hydraulic chamber and the second clamping hydraulic chamber when changing the gear ratio. A connecting oil passage.

  According to a second aspect of the present invention, in addition to the configuration of the first aspect, the hydraulic pressure of any one of the clamping hydraulic chambers that applies thrust to the movable piece of any one of the pulleys having the shift hydraulic chamber, The maximum pressure obtained from the maximum value of the torque and the maximum pressure of the hydraulic pressure in the shifting hydraulic chamber obtained from the maximum value of the belt winding radius of the one pulley are the same. The pressure receiving area of the movable piece that receives the hydraulic pressure of the pressure hydraulic chamber and the pressure receiving area of the third movable piece that receives the hydraulic pressure of the shifting hydraulic chamber are configured.

  According to a third aspect of the present invention, in addition to the configuration of the first or second aspect, the shift hydraulic chamber is provided at a side of the secondary pulley, and receives the hydraulic pressure of the second clamping hydraulic chamber. The pressure receiving area of the movable piece is configured to be narrower than the pressure receiving area of the first movable piece that receives the hydraulic pressure of the first clamping hydraulic chamber.

  The invention according to claim 4 includes a primary pulley and a secondary pulley that are rotatably provided, and a belt wound around the primary pulley and the secondary pulley, and a speed change between the primary pulley and the secondary pulley. In the hydraulic control device for a belt-type continuously variable transmission configured to change the ratio steplessly, the primary pulley has a first movable piece movable along the direction of the rotation center line, There is provided a first clamping pressure hydraulic chamber that generates a clamping pressure that is supplied and presses the first movable piece against the belt in a direction along the rotation center line, and the secondary pulley extends along the rotation center line direction. And a second movable piece that can be moved, and is supplied with oil to press the second movable piece against the belt in a direction along the rotation center line. There is provided a second hydraulic pressure chamber for pinching, and a third movable piece that contacts the first movable piece and is movable in a direction along the rotation center line, and a second movable piece. A fourth movable piece movable in a direction along the rotation center line, and oil is supplied to give thrust in the direction along the rotation center line to the third movable piece and the first movable piece. And a first hydraulic pressure chamber for controlling the gear ratio.

  According to a fourth aspect of the present invention, in addition to the above-described configuration, oil is supplied to apply thrust in a direction along the rotation center line to the fourth movable piece and the second movable piece. The second shifting hydraulic chamber for controlling the ratio, the first clamping hydraulic chamber, and the second clamping hydraulic chamber are connected, and the first clamping pressure is changed when the transmission ratio is changed. A connecting oil passage for transferring oil back and forth between the hydraulic chamber and the second clamping hydraulic chamber, the hydraulic pressure of one of the clamping hydraulic chambers, and a maximum pressure obtained from the maximum value of the transmission torque; The one pinch is set so that the maximum pressure of the hydraulic pressure in the speed change hydraulic chamber provided in any one pulley obtained from the maximum value of the belt winding radius in any one pulley is the same. Pressure receiving area of the movable piece that receives the hydraulic pressure of the pressure hydraulic chamber, and It is characterized in that the pressure receiving area of the movable piece that receives the hydraulic pressure of the shifting hydraulic chamber provided Re or the one pulley is configured.

  The invention according to claim 5 includes a primary pulley and a secondary pulley that are rotatably provided, and a belt wound around the primary pulley and the secondary pulley, and a speed change between the primary pulley and the secondary pulley. In the hydraulic control device for a belt-type continuously variable transmission configured to change the ratio steplessly, the primary pulley has a first movable piece movable along the direction of the rotation center line, There is provided a first clamping pressure hydraulic chamber that generates a clamping pressure that is supplied and presses the first movable piece against the belt in a direction along the rotation center line, and the secondary pulley extends along the rotation center line direction. And a second movable piece that can be moved, and is supplied with oil to press the second movable piece against the belt in a direction along the rotation center line. Second squeezing pressure chamber is provided for generating, and a third movable piece movable in a direction along the rotation center line in contact with the first movable piece.

  According to a fifth aspect of the present invention, in addition to the above-described configuration, the fourth movable piece that is in contact with the second movable piece and is movable in a direction along the rotation center line, and oil is supplied to the third movable piece. The first movable piece and the first movable piece are given a thrust in the direction along the rotation center line, whereby the first shift hydraulic chamber for controlling the transmission ratio and the oil are supplied to the fourth movable piece. And by applying a thrust in the direction along the rotation center line to the second movable piece, the second shift hydraulic chamber for controlling the gear ratio, the first clamping hydraulic chamber, and the second And a connecting oil passage for connecting oil between the first clamping hydraulic chamber and the second clamping hydraulic chamber when connecting the clamping hydraulic chamber and changing the speed ratio, A first oil pump that discharges oil to be supplied to the first shift hydraulic chamber; And a second oil pump that discharges oil supplied to the hydraulic chamber and a third oil pump that discharges oil supplied to the first clamping hydraulic chamber and the second clamping hydraulic chamber. It is characterized by being provided.

  According to the first aspect of the invention, when changing the gear ratio of the belt-type continuously variable transmission, the oil flows back and forth between the first clamping pressure hydraulic chamber and the second clamping pressure hydraulic chamber, Oil is not discharged to the outside and energy loss of oil can be suppressed. The transmission hydraulic chamber is provided in either the primary pulley or the secondary pulley, and when the hydraulic pressure of the transmission hydraulic chamber is changed, the first clamping hydraulic chamber and the second clamping hydraulic chamber are changed. Oil goes back and forth between them. Therefore, it is not necessary to provide a dedicated actuator for oil to move back and forth between the first clamping hydraulic chamber and the second clamping hydraulic chamber, thereby avoiding the complexity of the structure.

  According to the invention of claim 2, in addition to obtaining the same effect as that of the invention of claim 1, in order to obtain the pressure receiving area using the maximum pressure, the pressure receiving area for generating the necessary thrust is relatively narrow. can do. Therefore, the flow rate of the oil supplied to the clamping hydraulic chamber and the transmission hydraulic chamber can be relatively reduced, and the energy loss of the oil can be further reduced.

  According to the invention of claim 3, in addition to obtaining the same effect as that of the invention of claim 1 or 2, when the hydraulic pressure of the shifting hydraulic chamber is made relatively high, the movable piece of either pulley is pressed. As a result, the belt has a relatively large radius of wrapping around the pulley, and the belt has a relatively small radius of wrap around the other pulley. On the other hand, when the hydraulic pressure in the speed change hydraulic chamber is relatively low, the difference between the pressure receiving area of the movable piece provided in one pulley and the pressure receiving area of the movable piece provided in the other pulley causes the other When the movable piece of the pulley is pressed, the belt winding radius of the pulley is relatively increased, and the belt winding radius of one pulley is relatively reduced.

  According to the invention of claim 4, when changing the gear ratio in the belt-type continuously variable transmission, the oil flows back and forth between the first clamping hydraulic chamber and the second clamping hydraulic chamber, Oil is not discharged to the outside and energy loss of oil can be suppressed. The speed change hydraulic chamber is provided in both the primary pulley and the secondary pulley, and the amount of oil in both speed change hydraulic chambers is controlled to control the thrust applied to the third movable piece and the fourth movable piece. Then, the first movable piece and the second movable piece move to change the gear ratio, and the oil moves back and forth between the first clamping pressure hydraulic chamber and the second clamping pressure hydraulic chamber. Therefore, it is not necessary to provide a dedicated actuator for oil to move back and forth between the first clamping hydraulic chamber and the second clamping hydraulic chamber, and it is possible to avoid a complicated structure or an increase in weight.

  According to the invention of claim 5, when changing the gear ratio in the belt type continuously variable transmission, the oil flows back and forth between the first clamping pressure hydraulic chamber and the second clamping pressure hydraulic chamber, Oil is not discharged to the outside and energy loss of oil can be suppressed. Further, the shifting hydraulic chamber is provided in both the primary pulley and the secondary pulley, and when the oil amount in both the shifting hydraulic chambers is controlled, the thrust applied to the third movable piece and the fourth movable piece changes. Then, the first movable piece and the second movable piece move to change the gear ratio, and the oil moves back and forth between the first clamping pressure hydraulic chamber and the second clamping pressure hydraulic chamber. Therefore, it is not necessary to provide a dedicated actuator for oil to move back and forth between the first clamping hydraulic chamber and the second clamping hydraulic chamber, thereby avoiding the complexity of the structure. In addition, since an oil pump is connected to each hydraulic chamber, the discharge amount of each oil pump can be controlled separately based on the amount of oil required in each hydraulic chamber, and energy loss can be further reduced. .

It is a figure which shows the 1st specific example of the hydraulic control apparatus of the belt type continuously variable transmission of this invention. It is a figure which shows the 2nd specific example of the hydraulic control apparatus of the belt type continuously variable transmission of this invention. It is a figure which shows the 3rd specific example of the hydraulic control apparatus of the belt type continuously variable transmission of this invention.

  The belt type continuously variable transmission according to the present invention is arranged in a power transmission path from a power source to a driven member, and the gear ratio between the primary pulley and the secondary pulley is continuously variable, that is, continuously. It is configured to be changeable. More specifically, the belt-type continuously variable transmission according to the present invention includes a shifting hydraulic chamber and a clamping hydraulic chamber, and controls the flow rate or hydraulic pressure of oil supplied from the hydraulic source to the shifting hydraulic chamber. Thus, the transmission ratio is controlled, and the transmission torque is controlled by controlling the flow rate or hydraulic pressure of the oil supplied from the hydraulic source to the clamping hydraulic chamber. The movable piece according to the present invention is configured to move in a direction along the rotation center line, and is a component that generates thrust upon receiving hydraulic pressure. The belt type continuously variable transmission according to the present invention is disposed, for example, in a power transmission path from a driving force source of a vehicle to driving wheels. Hereinafter, specific examples of the hydraulic control device for the belt type continuously variable transmission according to the present invention will be sequentially described.

(First example)
A first specific example of a hydraulic control device for a belt-type continuously variable transmission will be described with reference to FIG. The belt-type continuously variable transmission 1 has a primary pulley 2 and a secondary pulley 3, and an endless belt 4 is wound around the primary pulley 2 and the secondary pulley 3. The primary pulley 2 is provided on a primary shaft 5, and the primary pulley 2 has a fixed piece 6 and a movable piece 7. The fixed piece 6 rotates integrally with the primary shaft 5 but does not move in the direction along the rotation center line of the primary shaft 5. On the other hand, the movable piece 7 is configured to rotate integrally with the primary shaft 5 and to move in a direction along the rotation center line of the primary shaft 5.

  In addition, a partition wall 8 configured to rotate integrally with the primary shaft 5 is attached to the primary shaft 5, and a first clamping pressure hydraulic chamber 9 is formed between the partition wall 8 and the movable piece 7. ing. The partition wall 8 partitions the internal space of the casing in which the belt-type continuously variable transmission 1 is disposed from the first clamping pressure hydraulic chamber 9. More specifically, the partition wall 8 is formed in an annular shape, and the primary shaft 5 and the partition wall 8 are arranged coaxially. The primary shaft 5 is rotatably supported by two bearings 10 arranged at different positions in the direction along the rotation center line, and the partition wall 8 is in contact with the inner ring of one of the bearings 10. Thus, when the partition wall 8 contacts the bearing 10, the partition wall 8 and the fixed piece 6 are positioned in a direction along the rotation center line of the primary shaft 5. A seal ring 11 is attached to the outer peripheral end of the partition wall 8.

  On the other hand, the movable piece 7 is formed with a cylindrical portion 12 extending in the direction along the rotation center line, and the seal ring 11 comes into contact with the inner peripheral surface of the cylindrical portion 12, thereby Pressure oil is prevented from leaking from the clamping hydraulic chamber 9. Further, the movable piece 7 and the primary shaft 5 are supplied with pressure oil to the first clamping pressure hydraulic chamber 9 or an oil passage (not shown) for discharging the pressure oil from the first clamping pressure chamber 9. Is provided. In this way, the first clamping hydraulic chamber 9 is sealed in a liquid-tight manner, and the hydraulic pressure in the first clamping hydraulic chamber 9 acts on the movable piece 7, and the movable piece 7 serves as the rotation center of the primary shaft 5. A thrust is generated that pushes in a direction along the line. More specifically, a thrust force is generated in such a direction that the movable piece 7 is pressed against the fixed piece 6, and the belt 4 is sandwiched between the movable piece 7 and the fixed piece 6.

  The secondary pulley 3 is provided on the secondary shaft 13. The rotation center line of the secondary shaft 13 is parallel to the rotation center line of the primary shaft 5. The secondary pulley 3 has a fixed piece 14 and a movable piece 15. The fixed piece 14 is configured to rotate integrally with the secondary shaft 13 and not move in a direction along the rotation center line of the secondary shaft 13. On the other hand, the movable piece 15 is configured to rotate integrally with the secondary shaft 13 and be movable in a direction along the rotation center line of the secondary shaft 13.

  Further, a cylinder 16 configured to rotate integrally with the secondary shaft 13 is attached to the secondary shaft 13. The secondary shaft 13 is rotatably supported by two bearings 17 arranged at different positions in the direction along the rotation center line. The cylinder 16 is brought into contact with the inner ring of one of the bearings 17 so that the cylinder 16 and the fixed piece 14 are positioned in a direction along the rotation center line of the secondary shaft 13. On the other hand, the movable piece 15 is formed with a cylindrical portion 18 extending along the center line direction, and a part of the cylindrical portion 18 is disposed inside the cylinder 16. Further, a partition wall 19 is provided inside the cylinder 16, and a second clamping hydraulic chamber 20 is formed between the partition wall 19 and the movable piece 15. More specifically, the partition wall 19 is formed in an annular shape, and the secondary shaft 13 and the partition wall 19 are arranged coaxially. A seal ring 21 is attached to the outer peripheral end of the partition wall 19.

  The seal ring 21 is in contact with the inner peripheral surface of the cylindrical portion 18, thereby preventing pressure oil from leaking from the second clamping hydraulic chamber 20. The hydraulic pressure in the second clamping hydraulic chamber 20 acts on the movable piece 15 to generate a thrust that presses the movable piece 15 in a direction along the rotation center line of the secondary shaft 13. More specifically, a thrust force that presses the movable piece 15 against the fixed piece 14 is generated, and the belt 4 is sandwiched between the movable piece 15 and the fixed piece 14. Further, the movable piece 15 and the secondary shaft 13 are supplied with pressure oil to the second clamping pressure hydraulic chamber 20 or an oil passage (not shown) for discharging the pressure oil from the second clamping pressure hydraulic chamber 20. Is provided. Further, a piston 22 is disposed between the cylinder 16 and the partition wall 19.

  The piston 22 is formed in an annular shape, and a seal ring 23 is attached to the inner peripheral end of the piston 22 and a seal sing 24 is attached to the outer peripheral end. The piston 22 can move in the direction along the rotation center line in a state where the seal singe 24 is in contact with the inner peripheral surface of the cylinder 16 and the seal ring 23 is in contact with the partition wall 19. Further, the piston 22 and the cylindrical portion 18 of the movable piece 15 are configured so as to be able to contact or leave. In this way, a speed change hydraulic chamber 25 is formed between the piston 22 and the cylinder 16. That is, the transmission hydraulic chamber 25 is disposed on the side of the secondary pulley 3 in the direction along the rotation center line of the secondary shaft 13. Further, an oil passage for supplying pressure oil to the transmission hydraulic chamber 25 or discharging the pressure oil from the transmission hydraulic chamber 25 is formed in the movable piece 15 and the secondary shaft 13. The hydraulic pressure in the shifting hydraulic chamber 25 acts on the piston 22 to generate a thrust that presses the piston 22 in a direction along the rotation center line of the secondary shaft 13. Since the piston 22 is in contact with the movable piece 15, the thrust of the piston 22 is transmitted to the movable piece 15.

  Next, the configuration of the hydraulic circuit connected to the first clamping hydraulic chamber 9 and the second clamping hydraulic chamber 20, and further to the transmission hydraulic chamber 25 will be described. An oil pump OP that is driven by the power of the power source and sucks oil from the oil pan 26 and discharges the oil to the oil passage 27 is provided. A solenoid valve 28 is connected to the oil passage 27. The solenoid valve 28 has an input port 30 and an output port 31, and the input port 30 is connected to the oil passage 27. By controlling the solenoid valve 28, the input port 30 and the output port 31 can be connected or disconnected. Further, the output port 31 is connected to an oil passage 32, and the oil passage 32 is branched in two directions and connected to the first clamping pressure hydraulic chamber 9 and the second clamping pressure hydraulic chamber 20. Further, a solenoid valve 29 is connected to the oil passage 32. The solenoid valve 29 has an input port 33 and an output port 34, and the input port 33 is connected to the oil passage 32. An output port 34 is connected to the oil pan 26. By controlling the solenoid valve 29, the input port 33 and the output port 34 can be connected or disconnected.

  Further, the configuration of the hydraulic circuit connected to the shift hydraulic chamber 25 will be described. Solenoid valves 35 and 36 are connected to the oil passage 27. The solenoid valve 35 has an input port 37 and an output port 38, and the input port 37 is connected to the oil passage 29. By controlling the solenoid valve 35, the input port 37 and the output port 38 can be connected or disconnected. Further, the output port 38 is connected to an oil passage 39, and the oil passage 39 is connected to the shift hydraulic chamber 25. Further, a solenoid valve 36 is connected to the oil passage 39. The solenoid valve 36 has an input port 40 and an output port 41, and the input port 40 is connected to the oil passage 39. An output port 41 is connected to the oil pan 26. By controlling the solenoid valve 36, the input port 40 and the output port 41 can be connected or disconnected.

  The belt type continuously variable transmission 1 configured as described above is disposed in a power transmission path from a vehicle power source 42 to a drive wheel as a driven member. As the power source 42, at least one of an engine, an electric motor, a flywheel system, or the like can be used. Further, a fluid transmission device 43 and a forward / reverse switching device 44 can be provided in a power transmission path from the power source 42 to the primary shaft 5 of the belt type continuously variable transmission 1. The vehicle is provided with a sensor (not shown) for detecting the rotational speed of the power source, the vehicle speed, the acceleration request, the braking request, and the like. The vehicle is provided with an electronic control device (not shown) that processes the signal of the sensor. Based on the signal input to the electronic control unit, the required driving force in the vehicle is obtained. Based on the required driving force, the target torque of the power source, the target transmission ratio of the belt type continuously variable transmission, the target transmission torque, etc. Is determined. Then, a signal for controlling the solenoid valves 28, 29, 35, and 36 is output from the electronic control device, and the gear ratio and transmission torque of the belt type continuously variable transmission 1 are controlled.

  By the way, in the first specific example, both the second clamping hydraulic chamber 20 and the transmission hydraulic chamber 25 are provided in the secondary pulley 3, and the movable piece 7 that receives the hydraulic pressure of the first clamping hydraulic chamber 9 is provided. The pressure receiving area M1 is configured to be larger than the pressure receiving area M2 of the movable piece 15 that receives the hydraulic pressure of the second clamping hydraulic chamber 25. Here, the pressure receiving area is an area where the hydraulic pressure acts in a direction in which the movable pieces 7 and 15 are given thrust in the direction along the rotation center line, and specifically, an area in a plane orthogonal to the rotation center line. It is represented by

In the first specific example, in addition to the relationship between the pressure receiving areas M1 and M2,
Maximum thrust F1 = Maximum hydraulic pressure P1 x Pressure receiving area M (1)
Maximum thrust F2 = Maximum hydraulic pressure P2 x Pressure receiving area m (2)
Assuming that
Maximum hydraulic pressure P1 = Maximum hydraulic pressure P2 (3)
Thus, the pressure receiving area M of the movable piece 7 and the pressure receiving area m 2 of the piston 22 can be configured. Here, the maximum thrust F 1 is the maximum value of the thrust applied to the movable piece 7 of the primary pulley 2, and the maximum thrust F 2 is the maximum value of the thrust applied to the piston 22 of the secondary pulley 3. The maximum hydraulic pressure P1 is the maximum value of the hydraulic pressure in the first clamping pressure hydraulic chamber 9, and the maximum hydraulic pressure P2 is the maximum value of the hydraulic pressure in the shift hydraulic chamber 25.

  The maximum thrust F1 can be obtained, for example, as follows. First, the maximum transmission torque of the belt-type continuously variable transmission 1 is obtained from the maximum transmission ratio of the belt-type continuously variable transmission 1 and the maximum torque of the power source, and from the maximum transmission torque, the maximum value of necessary thrust, that is, the maximum Find the thrust F1. On the other hand, the maximum value of the thrust applied to the cylinder 22, that is, the maximum thrust F2 can be obtained from the maximum speed ratio of the belt type continuously variable transmission 1.

  Next, the control and operation of the belt type continuously variable transmission 1 will be described. As described above, the required driving force in the vehicle is obtained based on the signal input to the electronic control unit, and based on the required driving force, the target torque of the power source, the target gear ratio of the belt type continuously variable transmission 1 is obtained. Further, the target transmission torque and the like are determined. For convenience, the control based on the target transmission torque will be described first. When the solenoid valve 28 is controlled to connect the input port 30 and the output port 31, and the solenoid valve 29 is controlled to shut off the input port 33 and the output port 34, the oil in the oil passage 29 is The oil is supplied to the oil passage 32 via the solenoid valve 28. On the other hand, when the solenoid valve 28 is controlled to shut off the input port 30 and the output port 31 and the solenoid valve 29 is controlled to connect the input port 33 and the output port 34, the oil passage 32. The oil is discharged to the oil pan 26 via the solenoid valve 29.

  Further, when the solenoid valve 28 is controlled to shut off the input port 30 and the output port 31, and the solenoid valve 29 is controlled to shut off the input port 33 and the output port 34, the oil path 29 is changed to the oil path 32. No oil is supplied, and the oil in the oil passage 32 is not discharged to the oil pan 26. In this way, the hydraulic pressures of the first clamping pressure hydraulic chamber 9 and the second clamping pressure hydraulic chamber 20 are controlled. That is, the clamping pressure applied to the belt 4 in the primary pulley 2 is controlled, and the clamping pressure applied to the belt 4 in the secondary pulley 3 is controlled. Further, since the first clamping hydraulic chamber 9 and the second clamping hydraulic chamber 20 are connected by an oil passage 32, the hydraulic pressure of the first clamping hydraulic chamber 9 and the second clamping hydraulic chamber 20 are connected. The hydraulic pressure is the same.

  On the other hand, the hydraulic pressure in the shift hydraulic chamber 25 is controlled based on the target gear ratio of the belt type continuously variable transmission 1. Specifically, a thrust is generated in the piston 22 by the hydraulic pressure in the speed change hydraulic chamber 25, and the thrust is transmitted to the movable piece 15 to control the winding radius of the belt 4 in the primary pulley 2 and the secondary pulley 3. . For example, when downshifting to reduce the gear ratio of the belt type continuously variable transmission 1 is performed, the solenoid valve 36 is controlled to shut off the input port 40 and the output port 41, and the solenoid valve 35 outputs the input port 37 to the output. By controlling connection and disconnection with the port 38, the amount of oil supplied from the oil passage 27 to the oil passage 39 via the solenoid valve 35 is controlled. By performing this control, the flow rate of the oil retained in the shift hydraulic chamber 25 increases. On the other hand, when an upshift is performed to increase the gear ratio of the belt type continuously variable transmission 1, the solenoid valve 35 is controlled to shut off the input port 37 and the output port 38, and the input port 37 is shut off by the solenoid valve 36. By controlling the connection and disconnection between 40 and the output port 41, the amount of oil discharged from the gear shift hydraulic chamber 25 to the oil pan 26 via the solenoid valve 36 is controlled. By this control, the amount of oil held in the shift hydraulic chamber 25 is reduced.

  By the way, in the first specific example, the pressure receiving area M1 of the movable piece 7 is configured to be larger than the pressure receiving area M2 of the movable piece 15, and the thrust of the piston 22 is transmitted to the movable piece 15. ing. For this reason, when the input port 30 and the output port 31 of the solenoid valve 28 are closed and the input port 33 and the output port 34 of the solenoid valve 29 are closed, the hydraulic pressure of the shift hydraulic chamber 25 is relatively When the pressure decreases, the thrust generated in the movable piece 7 is larger than the thrust generated in the movable piece 15 due to the difference between the pressure receiving area M1 and the pressure receiving area M2. For this reason, the movable piece 7 moves rightward in FIG. In parallel with the movement of the movable piece 7, the oil in the second clamping pressure chamber 18 is sucked into the first clamping pressure chamber 9 via the oil passage 32, and the movable piece 15 is moved to the right in FIG. 1. Move in the direction. In this way, the winding radius of the belt 4 in the primary pulley 2 becomes relatively large, and the winding radius of the belt 4 in the secondary pulley 3 becomes relatively small. That is, a speed change in which the speed ratio of the belt type continuously variable transmission 1 is reduced, that is, an upshift is performed.

  On the other hand, when the input port 30 and the output port 31 of the solenoid valve 28 are closed and the input port 33 and the output port 34 of the solenoid valve 29 are closed, the hydraulic pressure in the speed change hydraulic chamber 25 is relatively low. When it becomes higher, the thrust of the cylinder 22 is transmitted to the movable piece 15 of the secondary pulley 3, and the movable piece 15 moves leftward in FIG. As a result, the winding radius of the belt 4 in the secondary pulley 3 becomes relatively large, the movable piece 7 moves to the left in FIG. 1, and the winding radius of the belt 4 in the primary pulley 2 is relatively small. Become. In addition, as the movable pieces 7 and 15 move, the oil in the first clamping hydraulic chamber 9 is supplied to the second clamping hydraulic chamber 20 via the oil passage 32. In this way, a shift in which the gear ratio of the belt type continuously variable transmission 1 is increased, that is, a downshift is performed. Then, the torque of the primary pulley 2 of the belt-type continuously variable transmission 1 is transmitted to the secondary pulley 3 via the belt 4, and the torque of the secondary pulley 3 is transmitted to the drive wheels.

  Thus, in the first specific example, since the pressure receiving area M1 is larger than the pressure receiving area M2, the oil amount in the transmission hydraulic chamber 25 is controlled, specifically, the oil amount in the transmission hydraulic chamber 25 is increased or increased. By reducing the oil, oil flows back and forth between the first clamping hydraulic chamber 9 and the second clamping hydraulic chamber 20 so that the gear ratio of the belt-type continuously variable transmission 1 can be changed. Has been. That is, the first clamping hydraulic chamber 9 and the second clamping hydraulic chamber 20 change the transmission ratio of the belt type continuously variable transmission 1 in addition to the function of controlling the transmission torque of the belt type continuously variable transmission 1. It has the function to do. Further, the control for changing the gear ratio of the belt-type continuously variable transmission 1 is performed in a state where the input port 30 and the output port 31 of the solenoid valve 28 are closed and the input port 33 and the output port 34 of the solenoid valve 29 are closed. In this case, oil flows back and forth between the first clamping pressure hydraulic chamber 9 and the second clamping pressure hydraulic chamber 20 via the oil passage 32, and the oil discharge amount or oil to the oil pan 26 or the outside The supply amount is relatively small. Therefore, it is possible to reduce oil energy loss when the belt type continuously variable transmission 1 is shifted.

  Furthermore, in the first specific example, by specifying the relationship between the pressure receiving area M 1 and the pressure receiving area M 2, the oil passage 32 is provided between the first clamping pressure hydraulic chamber 9 and the second clamping pressure hydraulic chamber 20. It is possible to suppress the increase in energy loss by causing the oil to go back and forth through. Therefore, compared to a configuration using a motor as described in JP-A-2005-226730, it can be configured with a normal hydraulic circuit without adding a special actuator, and the structure is complicated. Can be avoided.

  Furthermore, in the first specific example, when the pressure receiving area M 1 and the pressure receiving area m 2 are determined so as to satisfy the condition of the expression (3) on the assumption of the conditions of the expressions (1) and (2), the movable piece 7 and The pressure receiving area of the piston 22 can be made relatively narrow. Accordingly, the flow rate of oil supplied to the first clamping hydraulic chamber 9 and the shift hydraulic chamber 25 is relatively small, and energy loss due to a drop in hydraulic pressure in the oil passages 32 and 39 can be reduced.

  In the first specific example, a shifting hydraulic chamber is provided in either the primary pulley 2 or the secondary pulley 3, and a clamping hydraulic chamber is provided in both the primary pulley 2 and the secondary pulley 3. Any configuration may be used. Therefore, in the first specific example, in addition to the configuration of the belt-type continuously variable transmission shown in FIG. 1, the primary pulley 2 and the secondary pulley 3 are each provided with a clamping hydraulic chamber, and the primary pulley is used for shifting. Another configuration in which a hydraulic chamber is provided may be used. In this other configuration, the pressure receiving area of the clamping hydraulic chamber provided in the primary pulley is set smaller than the pressure receiving area of the clamping hydraulic chamber provided in the secondary pulley.

  In another configuration, when the hydraulic pressure in the speed change hydraulic chamber provided in the primary pulley is relatively low, the movable piece of the secondary pulley moves in a direction along the rotation center line, and the belt is wound around the secondary pulley. A shift, that is, a downshift, is performed in which the engagement radius increases and the movable piece of the primary pulley moves to decrease the belt engagement radius of the primary pulley. On the other hand, when the hydraulic pressure in the speed change hydraulic chamber provided in the primary pulley is relatively high, the movable piece of the primary pulley moves, the belt winding radius in the primary pulley increases, and the secondary pulley A shift, that is, an upshift is performed in which the movable piece moves and the belt winding radius of the secondary pulley becomes small.

  The first specific example corresponds to the invention of claims 1, 2, and 3. The correspondence between the first specific example and the configuration of the present invention will be described. The movable piece 7 is the first of the present invention. The movable piece 15 corresponds to the movable piece, the movable piece 15 corresponds to the second movable piece of the invention, the piston 22 corresponds to the third movable piece of the invention, and the first clamping pressure hydraulic chamber 9 corresponds to the invention. The first clamping hydraulic chamber 20 corresponds to the first clamping hydraulic chamber 20, the second clamping hydraulic chamber 20 of the present invention, and the shifting hydraulic chamber 25 corresponds to the shifting hydraulic chamber of the present invention. The oil passage 32 corresponds to the connection oil passage of the present invention.

(Second specific example)
A second specific example of the hydraulic control device for the belt-type continuously variable transmission will be described with reference to FIG. In the second specific example, the same components as those in the first specific example are denoted by the same reference numerals as those in the first specific example. The second specific example is different from the first specific example in that both the secondary pulley 3 and the primary pulley 2 are provided with speed change hydraulic chambers. Hereinafter, the configuration of the shift hydraulic chamber provided in the primary pulley 2 will be described in detail. First, a cylinder 45 configured to rotate integrally with the primary shaft 5 is provided. When the cylinder 45 is brought into contact with one bearing 10, the cylinder 45 and the fixed piece 6 are positioned in a direction along the rotation center line of the primary shaft 5. In the second specific example, the partition wall 8 is brought into contact with the cylinder 45, and the partition wall 8 and the fixed piece 6 are positioned in a direction along the rotation center line of the primary shaft 5.

  Further, a piston 46 is disposed inside the cylindrical portion of the cylinder 45. The piston 46 is formed in an annular shape, and a seal ring 47 is attached to the inner peripheral end of the piston 46, and a seal sing 48 is attached to the outer peripheral end. The piston 46 is configured to be movable in the direction along the rotation center line in a state where the seal singe 47 is in contact with the inner peripheral surface of the cylinder 45 and the seal ring 48 is in contact with the partition wall 8. Further, the piston 46 and the cylindrical portion 12 of the movable piece 7 are configured to be able to come into contact with and away from each other. In this way, a speed change hydraulic chamber 49 is formed between the piston 46 and the cylinder 45. That is, the speed change hydraulic chamber 49 is arranged on the side of the primary pulley 2 in the direction along the rotation center line of the primary shaft 5. Further, an oil passage (not shown) for supplying pressure oil to the transmission hydraulic chamber 49 or discharging the pressure oil from the transmission hydraulic chamber 49 is formed in the primary shaft 5.

  Further, the configuration of the hydraulic circuit connected to the shifting hydraulic chamber 49 will be described. A solenoid valve 50 is connected to the oil passage 27. The solenoid valve 50 has an input port 52 and an output port 53, and the input port 52 is connected to the oil passage 27. Further, the output port 53 is connected to an oil passage 54, and the oil passage 54 is connected to the shift hydraulic chamber 49. Further, a solenoid valve 51 is disposed in a path from the oil path 54 to the oil pan 26. The solenoid valve 51 has an input port 55 and an output port 56, and the input port 55 is connected to the oil passage 54. An output port 56 is connected to the oil pan 26.

  When the input port 52 and the output port 53 are connected or disconnected by controlling the solenoid valve 50, the flow rate of oil supplied from the oil passage 27 to the transmission hydraulic chamber 49 via the oil passage 54 is controlled. can do. Further, when the solenoid valve 51 is controlled so that the input port 55 and the output port 56 are connected or disconnected, the flow rate of oil discharged from the speed change hydraulic chamber 49 to the oil pan 26 via the oil passage 54 is controlled. be able to. The hydraulic pressure in the shifting hydraulic chamber 49 acts on the piston 46 to generate a thrust that presses the piston 46 in a direction along the rotation center line of the primary shaft 5. Specifically, the piston 46 is pressed toward the fixed piece 6, and the pressing force is transmitted to the movable piece 7. In the second specific example, the pressure receiving area of the movable piece 7 that receives the hydraulic pressure of the first clamping pressure hydraulic chamber 9 and the pressure receiving area of the movable piece 15 that receives the hydraulic pressure of the second clamping hydraulic chamber 20 are the same. It is configured.

  Also in the second specific example, the pressure receiving area M of the movable piece 7 and the pressure receiving area m 2 of the piston 22 can be determined so as to satisfy the expression (3) on the assumption of the expressions (1) and (2). . Here, the maximum thrust F 1 is the maximum value of the thrust applied to the movable piece 7 of the primary pulley 2, and the maximum thrust F 2 is the maximum value of the thrust applied to the piston 22 of the secondary pulley 3. The maximum hydraulic pressure P1 is the maximum value of the hydraulic pressure in the first clamping pressure hydraulic chamber 9, and the maximum hydraulic pressure P2 is the maximum value of the hydraulic pressure in the shift hydraulic chamber 25. The pressure receiving area M is the area of the portion that receives the hydraulic pressure in the first clamping hydraulic chamber 9 and applies thrust to the movable piece 7. Further, the pressure receiving area m 2 is an area of a portion that receives the hydraulic pressure of the shifting hydraulic chamber 25 and applies thrust to the piston 22.

  The maximum thrust F1 can be obtained, for example, as follows. First, the maximum transmission torque of the belt-type continuously variable transmission 1 is obtained from the maximum transmission ratio of the belt-type continuously variable transmission 1 and the maximum torque of the power source, and from the maximum transmission torque, the maximum value of necessary thrust, that is, the maximum Find the thrust F1. On the other hand, the maximum thrust F2 can be obtained as follows, for example. First, the maximum value of the thrust applied to the cylinder 22, that is, the maximum thrust F2 is obtained from the maximum speed ratio of the belt type continuously variable transmission 1.

  On the other hand, in the second specific example, the pressure receiving area M of the movable piece 15 and the pressure receiving area m of the piston 46 can be configured so as to satisfy the relationships of the expressions (1), (2), and (3). . In such a configuration, the maximum thrust F1 is the maximum value of the thrust applied to the movable piece 15 of the secondary pulley 3, and the maximum thrust F2 is the maximum value of the thrust applied to the piston 49 of the primary pulley 2. The maximum hydraulic pressure P1 is the maximum value of the hydraulic pressure in the second clamping hydraulic chamber 20, and the maximum hydraulic pressure P2 is the maximum value of the hydraulic pressure in the shift hydraulic chamber 49.

  The maximum thrust F1 can be obtained, for example, as follows. First, the maximum transmission torque of the belt-type continuously variable transmission 1 is obtained from the maximum transmission ratio of the belt-type continuously variable transmission 1 and the maximum torque of the power source, and from the maximum transmission torque, the maximum value of necessary thrust, that is, the maximum Find the thrust F1. On the other hand, the maximum thrust F2 can be obtained as follows, for example. First, the maximum value of the thrust applied to the cylinder 22, that is, the maximum thrust F2 is obtained from the maximum speed ratio of the belt type continuously variable transmission 1.

  In the second specific example, on the premise of Expression (1) and Expression (2), the pressure receiving area M of the movable piece 7 and the pressure receiving area m of the piston 22 are configured so as to satisfy the relationship of Expression (3). Or assuming that the pressure receiving area M of the movable piece 15 and the pressure receiving area m of the piston 46 are configured so as to satisfy the relationship of the expression (3) on the premise of the expressions (1) and (2). One can be adopted.

  In the second specific example, the same operational effects as those of the first specific example can be obtained for the same components as in the first specific example. In the second specific example, the pressure receiving area of the movable piece 7 that receives the hydraulic pressure of the first clamping pressure hydraulic chamber 9 and the pressure receiving area of the movable piece 15 that receives the hydraulic pressure of the second clamping hydraulic chamber 20 are the same. Therefore, the gear ratio of the belt-type continuously variable transmission 1 is controlled by controlling the oil amount in the shift hydraulic chamber 49 in addition to controlling the oil amount in the shift hydraulic chamber 25. be able to.

  More specifically, when the solenoid valve 51 is controlled and the input port 55 and the output port 56 are shut off, the solenoid valve 50 is controlled and the input port 52 and the output port 53 are connected. Then, the amount of oil supplied from the oil passage 27 via the oil passage 32 to the speed change hydraulic chamber 49 increases. By this action, the hydraulic pressure in the transmission hydraulic chamber 49 is increased, and the thrust for pressing the piston 46 in the right direction in FIG. 2 is increased. The thrust of the piston 46 is transmitted to the movable piece 7 so that the belt 4 has a larger radius of wrap around the primary pulley 2 and the secondary pulley 3 has a smaller radius of wrap around the belt 4, that is, an upshift is performed. It is.

  On the other hand, when the solenoid valve 50 is controlled and the input port 52 and the output port 53 are shut off, the solenoid valve 51 is controlled and the input port 55 and the output port 56 are connected. The amount of oil discharged from the speed change hydraulic chamber 49 via the oil passage 54 to the oil pan 26 increases. As a result, the hydraulic pressure in the shifting hydraulic chamber 49 decreases, and the thrust that presses the piston 48 rightward in FIG. 2 decreases. On the other hand, when the solenoid valves 35 and 36 are controlled in parallel with the control of the solenoid valves 50 and 51, the amount of oil in the shifting hydraulic chamber 25 increases. As a result of the above-described control, the wrapping radius of the belt 4 in the secondary pulley 3 is increased, and a shift, that is, a downshift is generated in which the wrapping radius of the belt 4 in the primary pulley 2 is decreased. As described above, in the second specific example, the belt-type continuously variable transmission 1 performs a shift by controlling the hydraulic pressure in the shift hydraulic chamber 25 and the hydraulic pressure in the shift hydraulic chamber 49.

  In the second specific example, even if the hydraulic pressure in the transmission hydraulic chamber 25 and the hydraulic pressure in the transmission hydraulic chamber 49 are changed, the volume of the first clamping hydraulic chamber 9 does not change, and the second The volume of the clamping pressure hydraulic chamber 20 does not change. Accordingly, it is possible to reduce energy consumption due to oil flowing back and forth between the first clamping hydraulic chamber 9 and the second clamping hydraulic chamber 20. In the second specific example, since the pressure receiving area of the movable piece 7 and the pressure receiving area of the movable piece 15 are the same, when the belt-type continuously variable transmission 1 is shifted, No oil flows back and forth between the two clamping pressure hydraulic chambers 20. Therefore, when the speed ratio of the belt-type continuously variable transmission 1 is changed, it is possible to prevent the thrust of the movable piece 7 from being changed due to a change in the hydraulic pressure in the first clamping pressure hydraulic chamber 9, and the second clamping pressure It is possible to prevent the thrust of the movable piece 15 from changing due to a change in the hydraulic pressure in the hydraulic chamber 20. Therefore, the accuracy of the shift control of the belt type continuously variable transmission 1 is improved.

  This second specific example corresponds to the invention of claim 4, and the correspondence between the configuration of the second specific example and the configuration of the present invention will be described. The movable piece 7 is the first movable piece of the present invention. The movable piece 15 corresponds to the second movable piece of the present invention, the piston 46 corresponds to the third movable piece of the present invention, the piston 22 corresponds to the fourth movable piece of the present invention, One clamping hydraulic chamber 9 corresponds to the first clamping hydraulic chamber of the present invention, and the second clamping hydraulic chamber 20 corresponds to the second clamping hydraulic chamber of the present invention. The chamber 49 corresponds to the first shifting hydraulic chamber of the present invention, the shifting hydraulic chamber 25 corresponds to the second shifting hydraulic chamber of the present invention, and the oil passage 32 corresponds to the connecting oil passage of the present invention. It corresponds to.

(Third example)
Next, a third specific example of the hydraulic control device for the belt type continuously variable transmission will be described with reference to FIG. In the third specific example, the same components as those of the second specific example are denoted by the same reference numerals as those of the second specific example. Comparing the second specific example and the third specific example, the third specific example is different in that an oil pump for supplying oil to each hydraulic chamber is provided independently. Specifically, an oil pump OP1 that discharges oil to be supplied to the shift hydraulic chamber 25 is provided, and the oil discharged from the oil pump OP1 passes through the oil passage 27 and enters the input port 37 of the solenoid valve 35. It is comprised so that it may be supplied to. An oil pump OP2 that discharges oil supplied to the first clamping hydraulic chamber 9 and the second clamping hydraulic chamber 20 is provided, and the oil discharged from the oil pump OP2 passes through the oil passage 57. The solenoid valve 28 is configured to be supplied to the input port 30.

  Further, an oil pump OP3 for discharging oil to be supplied to the transmission hydraulic chamber 49 is provided, and the oil discharged from the oil pump OP3 is supplied to the input port 52 of the solenoid valve 50 via the oil path 58. It is configured to be. These oil pumps OP1, OP2, and OP3 are all configured to be driven by the power of the power source 42. Further, at least one of a clutch (not shown) for controlling transmission torque and a transmission (not shown) capable of changing a transmission ratio between these oil pumps OP1, OP2, OP3 and the power source 42. May be provided. If comprised in this way, the energy consumed for the drive of each oil pump can be controlled separately. In the third specific example, “a configuration in which the pressure receiving area M and the pressure receiving area m 2 are determined so that the maximum hydraulic pressure P1 = the maximum hydraulic pressure P2” is not set. Further, in the third specific example, the pressure receiving area M1 of the movable piece 7 and the pressure receiving area M2 of the movable piece 15 are configured to be the same.

  And in this 3rd example, the same effect as a 2nd example can be acquired about the same component as a 2nd example. In the third specific example, the hydraulic pressure generated by each oil pump is controlled to the minimum by controlling the clutch transmission torque or the transmission gear ratio based on the amount of oil required in each hydraulic chamber. Can do. Therefore, the energy required for driving the oil pump can be reduced.

  The third specific example corresponds to the invention of claim 5, and the correspondence between the configuration of the third specific example and the configuration of the present invention will be described. The movable piece 7 is the first movable piece of the present invention. The first clamping pressure hydraulic chamber 9 corresponds to the first clamping pressure hydraulic chamber of the present invention, the movable piece 15 corresponds to the second movable piece of the present invention, and the second clamping hydraulic chamber. 20 corresponds to the second clamping hydraulic chamber of the present invention, the shift hydraulic chamber 49 corresponds to the first shift hydraulic chamber of the present invention, and the shift hydraulic chamber 25 corresponds to the second hydraulic chamber of the present invention. The oil passage 32 corresponds to the connecting oil passage of the present invention, the oil pump OP3 corresponds to the first oil pump of the present invention, and the oil pump OP1 corresponds to the first oil pump of the present invention. The oil pump OP2 corresponds to the third oil pump of the present invention.

  Further, the solenoid valves 28, 29, 35, 36, 50, 51 used in the first to third specific examples are supplied or discharged by switching between energization (on) and non-energization (off). Either an on / off solenoid valve configured to control the flow rate or a duty solenoid valve configured to control the amount of oil supplied or discharged by controlling the ratio of the energization time. Further, in the first specific example to the third specific example, the oil pump is driven by the power source 42 that generates torque to be transmitted to the drive wheel, but the torque to be transmitted to the drive wheel is generated. Alternatively, a dedicated electric motor for driving the oil pump may be provided. Furthermore, in the first specific example to the third specific example, an oil pump is shown as a hydraulic source for supplying oil to each hydraulic chamber. However, an accumulator is used as a hydraulic source, and the oil stored in the accumulator is used for each hydraulic chamber. It is also possible to configure to supply to the hydraulic chamber.

  DESCRIPTION OF SYMBOLS 1 ... Belt type continuously variable transmission, 2 ... Primary pulley, 3 ... Secondary pulley, 7, 15 ... Movable piece, 9 ... 1st clamping hydraulic chamber, 20 ... 2nd clamping hydraulic chamber, 22, 46 ... Pistons 25, 49 ... hydraulic chambers for shifting, 32 ... oil passages, OP1, OP2, OP3 ... oil pumps.

Claims (5)

A primary pulley and a secondary pulley that are rotatably provided, and a belt that is wound around the primary pulley and the secondary pulley, and the speed change ratio between the primary pulley and the secondary pulley is continuously changed. In the hydraulic control device for a belt-type continuously variable transmission configured as described above,
The primary pulley has a first movable piece movable along the rotation center line direction, and is supplied with oil to generate a clamping pressure that presses the first movable piece against the belt in the direction along the rotation center line. A first clamping hydraulic chamber is provided,
The secondary pulley has a second movable piece movable along the rotation center line direction, and is supplied with oil to generate a clamping pressure that presses the second movable piece against the belt in the direction along the rotation center line. A second clamping pressure hydraulic chamber,
A third movable piece that is movable in a direction along the rotation center line in contact with the first movable piece or the second movable piece;
A shift hydraulic chamber that controls the speed ratio by supplying a thrust in a direction along the rotation center line to the third movable piece when oil is supplied;
The first clamping pressure hydraulic chamber and the second clamping pressure hydraulic chamber are connected, and the first clamping hydraulic chamber and the second clamping hydraulic chamber are connected when the speed ratio is changed. A hydraulic control device for a belt-type continuously variable transmission, comprising a connecting oil passage for moving oil back and forth.   The hydraulic pressure of any one of the clamping hydraulic chambers that gives thrust to the movable piece of any one of the pulleys having the shift hydraulic chamber, and the highest pressure obtained from the highest value of the transmission torque, The pressure receiving area of the movable piece that receives the hydraulic pressure of the one clamping pressure hydraulic chamber so that the maximum hydraulic pressure of the shifting hydraulic chamber obtained from the maximum value of the belt winding radius is the same; 2. The hydraulic control device for a belt-type continuously variable transmission according to claim 1, wherein a pressure receiving area of the third movable piece that receives the hydraulic pressure of the hydraulic chamber is configured. The speed change hydraulic chamber is provided on a side of the secondary pulley;
The pressure receiving area of the second movable piece that receives the hydraulic pressure of the second clamping hydraulic chamber is configured to be smaller than the pressure receiving area of the first movable piece that receives the hydraulic pressure of the first clamping hydraulic chamber. The hydraulic control device for a belt-type continuously variable transmission according to claim 1 or 2, characterized by the above. A primary pulley and a secondary pulley that are rotatably provided, and a belt that is wound around the primary pulley and the secondary pulley, and the speed change ratio between the primary pulley and the secondary pulley is continuously changed. In the hydraulic control device for a belt-type continuously variable transmission configured as described above,
The primary pulley has a first movable piece movable along the rotation center line direction, and is supplied with oil to generate a clamping pressure that presses the first movable piece against the belt in the direction along the rotation center line. A first clamping hydraulic chamber is provided,
The secondary pulley has a second movable piece movable along the rotation center line direction, and is supplied with oil to generate a clamping pressure that presses the second movable piece against the belt in the direction along the rotation center line. A second clamping pressure hydraulic chamber is provided,
A third movable piece that contacts the first movable piece and is movable in a direction along the rotation center line;
A fourth movable piece that contacts the second movable piece and is movable in a direction along the rotation center line;
A first shift hydraulic chamber that controls the gear ratio by supplying a thrust in a direction along the rotation center line to the third movable piece and the first movable piece by being supplied with oil;
A second shift hydraulic chamber that controls the gear ratio by supplying a thrust in a direction along the rotation center line to the fourth movable piece and the second movable piece by being supplied with oil;
The first clamping pressure hydraulic chamber and the second clamping pressure hydraulic chamber are connected, and the first clamping hydraulic chamber and the second clamping hydraulic chamber are connected when the speed ratio is changed. With a connecting oil passage that lets oil go back and forth,
It is the hydraulic pressure of either one of the clamping hydraulic chambers, and is applied to one of the pulleys obtained from the maximum pressure obtained from the maximum value of the transmission torque and the maximum value of the belt winding radius of the one of the pulleys. The pressure receiving area of the movable piece that receives the hydraulic pressure of the one clamping hydraulic chamber and the one of the pulleys are provided so that the maximum hydraulic pressure of the provided hydraulic chamber is the same. A hydraulic control device for a belt-type continuously variable transmission, characterized in that a pressure receiving area of a movable piece that receives the hydraulic pressure of a hydraulic pressure chamber is configured. A primary pulley and a secondary pulley that are rotatably provided, and a belt that is wound around the primary pulley and the secondary pulley, and the speed change ratio between the primary pulley and the secondary pulley is continuously changed. In the hydraulic control device for a belt-type continuously variable transmission configured as described above,
The primary pulley has a first movable piece movable along the rotation center line direction, and is supplied with oil to generate a clamping pressure that presses the first movable piece against the belt in the direction along the rotation center line. A first clamping hydraulic chamber is provided,
The secondary pulley has a second movable piece movable along the rotation center line direction, and is supplied with oil to generate a clamping pressure that presses the second movable piece against the belt in the direction along the rotation center line. A second clamping pressure hydraulic chamber is provided,
A third movable piece that contacts the first movable piece and is movable in a direction along the rotation center line;
A fourth movable piece that contacts the second movable piece and is movable in a direction along the rotation center line;
A first shift hydraulic chamber that controls the gear ratio by supplying a thrust in a direction along the rotation center line to the third movable piece and the first movable piece by being supplied with oil;
A second shift hydraulic chamber that controls the gear ratio by supplying a thrust in a direction along the rotation center line to the fourth movable piece and the second movable piece by being supplied with oil;
The first clamping pressure hydraulic chamber and the second clamping pressure hydraulic chamber are connected, and the first clamping hydraulic chamber and the second clamping hydraulic chamber are connected when the speed ratio is changed. With a connecting oil passage that lets oil go back and forth,
A first oil pump that discharges oil supplied to the first shift hydraulic chamber; a second oil pump that discharges oil supplied to the second shift hydraulic chamber; and the first clamping pressure A hydraulic control apparatus for a belt-type continuously variable transmission, wherein a hydraulic chamber and a third oil pump for discharging oil supplied to the second clamping hydraulic chamber are separately provided.

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