JP5310468B2 - Hydraulic control device for 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&amp;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, the pressure of the hydraulic oil pressure line, our Konawa are be supplied to the pulley oil chamber towards the thrust is small.

Note that hydraulic control devices for belt-type continuously variable transmissions are also described in Patent Documents 2 and 3 . In particular, 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 a movable piece of a primary pulley are provided, and a secondary pulley is provided. 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. .

The invention of claim 1 in order to achieve the above object, flop Raimaripu and Li are fixed piece integral with the rotation shaft of the primary pulley, the axis of rotation of the primary pulley so as to approach and away from the said fixing piece movable is constituted by a first movable piece which is provided, the cell Kandaripu Riga該integral to the secondary pulley rotation shaft fixing piece, the rotation of the secondary pulley so as to approach and away from the said fixed piece is constituted by a second movable piece which is movable in the axial, it has the primary pulley and the bell preparative be found wrapped around the secondary pulley, the winding of the belt in the primary pulley and said secondary pulley hydraulic control device odor speed change ratio behenate belt type is configured to change steplessly CVT by continuously changing the radius The first movable piece and the fixed piece in the primary pulley by pressing the first movable piece before Symbol from the oil pump is supplied oil in the direction along the rotation axis of the rotating during rotation central axis line of the primary pulley rotation before Symbol first squeezing pressure chamber Generating an clamping pressure sandwiching the belts, the second movable piece in the secondary pulley the oil is supplied to the rotational axis of the secondary pulley between the A second clamping hydraulic chamber for generating a clamping pressure for clamping the belt between the fixed piece and the second movable piece in the secondary pulley by pressing in a direction along a central axis; and A third movable piece that contacts the movable piece and is movable in a direction along a rotation center axis of the rotary shaft of the secondary pulley; and the oil is supplied to the second movable piece to the second movable piece. A transmission hydraulic chamber that changes the transmission ratio, a first clamping hydraulic chamber, and a second clamping hydraulic chamber by applying a thrust in a direction along the rotation center axis of the rotary shaft of the Dari pulley. A connecting oil passage for connecting and transferring the oil between the first clamping pressure hydraulic chamber and the second clamping pressure hydraulic chamber when changing the gear ratio, and a transmission hydraulic chamber And the other hydraulic passage for supplying the oil, and the transmission hydraulic chamber from the oil pump through the other oil passage in a state where the supply of the oil from the oil pump to the connecting oil passage is shut off. The first clamping pressure hydraulic pressure to be applied to the first movable piece obtained from the maximum torque transmitted by the belt type continuously variable transmission is configured so that the transmission ratio can be changed by supplying the oil to Maximum hydraulic pressure in the chamber The first clamping pressure hydraulic chamber has the same maximum hydraulic pressure in the transmission hydraulic chamber that is obtained from the maximum transmission ratio in the belt-type continuously variable transmission and should be given to the third movable piece. A pressure receiving area of the first movable piece that receives the hydraulic pressure and a pressure receiving area of the third movable piece that receives the hydraulic pressure of the shifting hydraulic chamber are configured, and the second pressure receiving pressure of the second clamping hydraulic chamber is configured. The pressure receiving area of the movable piece 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.

Incidentally, the reference example using the inventions, a fixing piece integral flop Raimaripu Li is the rotation shaft of the primary pulley, the axis of rotation of the primary pulley so as to approach and away from the said fixing piece is constituted by the first movable piece is movable, Se Kandaripu Riga該and fixing piece integral with the rotation shaft of the secondary pulley, the axis of rotation of the secondary pulley so as to approach and away from the said fixing piece a is constituted by a second movable piece that is movable, it has the primary pulley and the bell preparative be found wrapped around the secondary pulley, winding radius of the belt in between the primary pulley and the secondary pulley in the hydraulic control apparatus constructed have behenate belt type continuously variable transmission to change steplessly the speed change ratio by continuously changing the The first movable piece and the fixed piece in the primary pulley by pressing from the oil pump in the direction along the rotation axis of the rotating during rotation central axis line of the previous SL primary pulley previous SL first movable piece is supplied oil the first squeezing pressure chamber and, before Symbol secondary pulley previous SL second movable piece before Symbol secondary pulleys the oil is supplied to Generating an clamping pressure sandwiching the previous SL belts between the in the secondary pulley by pressing the along the rotation axis of the rotary centric axial said fixing piece and a second for Generating an clamping pressure sandwiching the previous SL belts between the second movable piece and squeezing hydraulic chamber, a pre-Symbol third movable piece movable in the direction along the rotation axis of the rotating during rotation central axis line of the previous SL primary pulley in contact with the first movable piece, in contact with the second movable piece to the previous Symbol of the secondary pulley times A fourth movable piece which is movable in a direction along the axis of rotation in the heart axis, the OIL is supplied in the rotation shaft of the prior SL primary pulley in the first friendly dynamic piece and the third allowed Dohen by giving the direction of thrust along during rotation central axis line, the first and the shifting hydraulic chamber to change the gear ratio, the second movable piece and the fourth movable piece the oil is supplied By applying thrust in the direction along the rotation center axis of the rotation shaft of the secondary pulley, the second transmission hydraulic chamber for changing the transmission ratio, the first clamping hydraulic chamber, and the second clamping hydraulic chamber. And a connecting oil passage for connecting the oil to and from the first clamping hydraulic chamber and the second clamping hydraulic chamber when changing the transmission gear ratio. , The hydraulic pressure in one of the clamping hydraulic chambers and obtained from the maximum value of the transmission torque And the maximum pressure of the hydraulic pressure in the shifting hydraulic chamber provided in one of the pulleys obtained from the maximum value of the wrapping radius of the belt in one of the pulleys is the same. The pressure receiving area of the movable piece that receives the hydraulic pressure of one of the clamping pressure hydraulic chambers, and the pressure receiving area of the movable piece that receives the hydraulic pressure of the speed change hydraulic chamber provided in one of the pulleys are configured. it is characterized in Rukoto. In addition to this, another example of the present invention provides another oil passage for supplying the oil to the second shift hydraulic chamber and the oil to the second shift hydraulic chamber. Further, another oil passage is provided.

Note also, and other references examples utilizing this inventions, flop Raimaripu Li is integral with the fixed piece to a rotating shaft of the primary pulley, the primary pulley so as to approach and away from the said fixing piece is constituted by the first movable piece is movable to the rotating shaft, integral with the fixed piece to a rotating shaft of cell Kandaripu Riga該secondary pulley, the secondary pulley so as to approach and away from the said fixing piece of which is constituted by a second movable piece is movable on the rotary shaft, having said primary pulley and said bell preparative be found wrapped around the secondary pulley, the belt in said secondary pulley and the primary pulley the hydraulic control device for the winding radius of consists of speed change ratio so as to change steplessly by continuously changing behenate belt type continuously variable transmission Oite, wherein the oil pump and the fixed piece in the primary pulley by pressing in the direction along the rotation centric axis of the rotating shaft before Symbol primary pulley previous SL first movable piece is supplied oil first a first squeezing pressure chamber Generating an clamping pressure sandwiching the previous SL belts between the first movable piece, the oil before the previous SL second movable piece in the previous SL secondary pulleys is supplied SL Generating an clamping pressure sandwiching the previous SL belts between the fixing piece and the second movable piece in the secondary pulley by pressing in the direction along the rotation axis of the rotating during rotation central axis line of the secondary pulley a second squeezing pressure chamber, a pre Symbol third movable piece movable in the direction along the rotation axis of the rotating during rotation central axis line of the previous SL primary pulley in contact with the first movable piece, the second movable The secondary plug A fourth movable piece movable in the direction along the rotation center axis of the rotation axis of the roller, and the rotation center axis of the rotation axis of the primary pulley supplied to the first movable piece and the third movable piece by supplying the oil The first transmission hydraulic chamber for changing the transmission gear ratio by applying a thrust in the direction along the axis, and the rotation shaft of the secondary pulley supplied to the second movable piece and the fourth movable piece by supplying the oil Connecting the second shifting hydraulic chamber, the first clamping hydraulic chamber, and the second clamping hydraulic chamber to change the gear ratio by applying a thrust in the direction along the rotation center axis of And a connecting oil path for transferring the oil back and forth between the first clamping pressure hydraulic chamber and the second clamping hydraulic chamber when changing the transmission ratio, and the first transmission hydraulic pressure The first oil pump that discharges oil supplied to the chamber A second oil pump that discharges oil to be supplied to the second shifting hydraulic chamber, and a third oil pump that discharges oil to be supplied to the first clamping hydraulic chamber and the second clamping hydraulic chamber. have an oil pump is characterized in Rukoto.

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. Thus, it finished without providing the actuator for hexa can rows for oil between a first squeezing pressure chamber and a second squeezing pressure chamber only, can be prevented from being complicated in structure. Further, when the hydraulic pressure in the speed change hydraulic chamber is relatively high, the movable piece of one of the pulleys is pressed, and the belt winding radius in the pulley becomes relatively large, and the belt in the other pulley A shift occurs in which the winding radius is relatively small. 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 reference example using the present invention, when the gear ratio is changed by the belt type continuously variable transmission, the oil flows back and forth between the first clamping hydraulic chamber and the second clamping hydraulic chamber. Thus, the oil is not discharged to the outside, and the energy loss of the 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.

Furthermore, according to another reference example using the present invention, when changing the gear ratio in the belt-type continuously variable transmission, between the first clamping hydraulic chamber and the second clamping hydraulic chamber. Oil flows back and forth, and the oil is not discharged to the outside, so that energy loss of the 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. .

Is a diagram illustrating an example of a hydraulic control device for belts type continuously variable transmission according to this inventions. Is a diagram showing another example of a hydraulic control device for belts type continuously variable transmission according to this inventions. Is a diagram showing still another example of a hydraulic control device for belts type continuously variable transmission according to this inventions.

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, examples of the hydraulic control device for the belt-type continuously variable transmission according to the present invention will be sequentially described.

Figure 1 shows one example of a hydraulic control device for belts type continuously variable transmission according to the present invention. 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 is generated in such a direction as to press the movable piece 7 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 27 . 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 example shown in FIG. 1 , the second clamping hydraulic chamber 20 and the transmission hydraulic chamber 25 are both provided in the secondary pulley 3 and receive the hydraulic pressure of the first clamping hydraulic chamber 9. 7 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 20 . 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

Further , in the example shown in FIG. 1, 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, from the maximum speed ratio of the belt type continuously variable transmission 1, the maximum value of the thrust applied to the piston 22 , that is, the maximum thrust F2 can be obtained.

  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 speed ratio of the belt type continuously variable transmission 1 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, by controlling the solenoid valve 28 to shut off the input port 30 and output port 31, and, when blocking the input port 33 and output port 34 by controlling the solenoid valve 29, the oil passage 27 or et oil passage 32 Oil is not supplied to the oil pan, 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 a downshift is performed you increase the gear ratio of the belt type continuously variable transmission 1, by controlling the solenoid valve 36 to shut off the input port 40 and output port 41, an input port 37 by the solenoid valve 35 By controlling connection and disconnection with the output 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. In contrast, when performing an upshift you reduce the gear ratio of the belt type continuously variable transmission 1, and cut off the input port 37 and output port 38 by controlling the solenoid valve 35, the input by the solenoid valve 36 By controlling connection and disconnection between the port 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.

Incidentally, in the example shown in Figure 1 of this, towards the pressure receiving area M1 of the movable piece 7 is configured 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 configured It has become. 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 becomes lower moving, because thrust generated by Rika Dohen 7 by the difference between the pressure receiving area M1 and the pressure receiving area M2 was larger than the thrust generated by the movable piece 15, to the right movable piece 7 in FIG. 1 To do. In parallel with the movement of the movable piece 7, oil in the second clamping pressure hydraulic chamber 20 is sucked into the first clamping pressure hydraulic chamber 9 via the oil passage 32, and the movable piece 15 is moved to the right in FIG. 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 piston 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 example shown in FIG. 1, 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. Alternatively, 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. It is configured. 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.

Further , in the example shown in FIG. 1, by specifying the relationship between the pressure receiving area M <b> 1 and the pressure receiving area M <b> 2, an oil path is formed between the first clamping pressure hydraulic chamber 9 and the second clamping pressure hydraulic chamber 20. 32 was hexa can rows for oil through it is possible to suppress an increase in energy loss. 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.

The example shown in Figure 1 of this, the shifting hydraulic chamber to one of the primary pulley 2 or secondary pulley 3 is provided, and, squeezing hydraulic chamber is provided on both the primary pulley 2 and secondary pulley 3 Any configuration may be used. Therefore , 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 provided with a transmission hydraulic chamber. Another configuration may be used. In this alternative configuration, than the pressure-receiving area of the squeezing pressure chamber provided in the secondary pulley pressure receiving surface product of squeezing hydraulic chamber provided in the primary pulley is set narrower.

  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.

In the example shown in Figure 1 of this, to describe the correspondence between the configuration of the present invention, the movable piece 7 is equivalent to the first movable piece of the present invention, the movable piece 15, the second movable piece of the present invention The piston 22 corresponds to the third movable piece of the present invention, the first clamping pressure hydraulic chamber 9 corresponds to the first clamping hydraulic chamber of the present invention, and the second clamping hydraulic chamber 20. This corresponds to the second clamping pressure hydraulic chamber of the present invention, the shift hydraulic chamber 25 corresponds to the shift hydraulic chamber of the present invention, and the oil passage 32 corresponds to the connecting oil passage of the present invention.

Figure 2 shows another example of a hydraulic control device for belts type continuously variable transmission according to the present invention. In the example shown in Figure 2 of this, for the same configuration as the example shown in FIG. 1 are denoted by the same reference numerals as in FIG. In the example shown in Figure 2 of this, that the shifting hydraulic chambers are provided in both the secondary pulley 3 and the primary pulley 2 is different from the example shown in FIG. 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 example shown in FIG. 2 , 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 example shown in FIG. 2, 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 obtained. It is configured identically.

In the example shown in FIG. 2, the pressure receiving area M of the movable piece 7 and the pressure receiving area m 2 of the piston 22 may be determined so as to satisfy the expression (3) on the assumption of the expressions (1) and (2). it can. 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 piston 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 example shown in FIG. 2, the pressure receiving area M of the movable piece 15 and the pressure receiving area m of the piston 46 may be configured so as to satisfy the relationships of the expressions (1), (2), and (3). it can. 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, maximum thrust F2 is the maximum value of the thrust force applied to the piston 46 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 piston 46 , that is, the maximum thrust F2 is obtained from the maximum speed ratio of the belt type continuously variable transmission 1.

In the example shown in FIG. 2, the pressure receiving area M of the movable piece 7 and the pressure receiving area m 2 of the piston 22 are configured so as to satisfy the relationship of Expression (3) on the assumption of Expression (1) and Expression (2). 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). At least one of them can be employed.

In the example shown in Figure 2 of this, the same components as the example shown in FIG. 1, it produces the same effects as the example shown in FIG. In the example shown in FIG. 2, the pressure receiving area of the movable piece 7 that receives the hydraulic pressure of the first clamping 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 as follows. Since it is set to be the same, the oil ratio in the transmission hydraulic chamber 49 is controlled, and the oil ratio in the transmission hydraulic chamber 49 is controlled to control the gear ratio of the belt type continuously variable transmission 1. can do.

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. As a result, the amount of oil supplied from the oil passage 27 via the oil passage 54 to the shifting 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. This action, hydraulic pressure is reduced in the shifting hydraulic chamber 49, the thrust for pressing the right direction piston 46 in FIG. 2 is reduced. 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 that decreases the wrapping radius of the belt 4 in the primary pulley 2. Thus, in the example shown in FIG. 2, by controlling the hydraulic pressure of the hydraulic and shifting hydraulic chamber 49 of the shifting hydraulic chamber 25, speed change of the belt type continuously variable transmission 1 is performed.

In the example shown in Figure 2 of this, changing the hydraulic pressure in the hydraulic pressure and shifting hydraulic chamber 49 of the shifting hydraulic chamber 25, the volume of the first squeezing pressure chamber 9 does not change, and, The volume of the second 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 example shown in FIG. 2, 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, Oil does not flow to and from the second clamping hydraulic chamber 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.

Example shown in FIG. 2 of this and will be described the correspondence between the configuration of the present invention, the movable piece 7 is equivalent to the first movable piece of the present invention, the movable piece 15, corresponding 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, and the first clamping pressure hydraulic chamber 9 serves as the first clamping pressure of the present invention. The second clamping hydraulic chamber 20 corresponds to the hydraulic chamber, the second clamping hydraulic chamber 20 of the present invention, and the shifting hydraulic chamber 49 corresponds to the first shifting hydraulic chamber of the present invention. The shift hydraulic chamber 25 corresponds to the second shift hydraulic chamber of the present invention, and the oil passage 32 corresponds to the connection oil passage of the present invention.

3, are further shows another example of a hydraulic control device for belts type continuously variable transmission according to the present invention. In the example shown in Figure 3 of this, the same components as in the example shown in FIG. 2 are denoted by the same reference numerals as FIG. Comparing the example shown in FIG. 2 with the example shown in FIG. 3, the example shown in FIG. 3 is different in that an oil pump that supplies 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 example shown in FIG. 3 , “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. In the example shown in FIG. 3, 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.

Then, in the example shown in Figure 3 of this, the same components as in the example shown in FIG. 2 is obtained the same effects as the example shown in FIG. In the example shown in FIG. 3, 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. be able to. Therefore, the energy required for driving the oil pump can be reduced.

Example shown in FIG. 3 of this and will be described the correspondence between the configuration of the present invention, the movable piece 7 is equivalent to the first movable piece of the present invention, the first squeezing pressure chamber 9, first the present invention 1 is equivalent to a clamping pressure hydraulic chamber, the movable piece 15 is equivalent to a second movable piece of the present invention, and the second clamping pressure hydraulic chamber 20 is equivalent to a second clamping pressure hydraulic chamber of the present invention. The shift hydraulic chamber 49 corresponds to the first shift hydraulic chamber of the present invention, the shift hydraulic chamber 25 corresponds to the second shift hydraulic chamber of the present invention, and the oil passage 32 corresponds to the present invention. The oil pump OP3 corresponds to the connection oil passage, the oil pump OP1 corresponds to the first oil pump of the present invention, the oil pump OP1 corresponds to the second oil pump of the present invention, and the oil pump OP2 corresponds to the first oil pump of the present invention. 3 oil pump.

Further, the solenoid valves 28,29,35,36,50,51 used in the example shown in FIG. 3 to no example shown in FIG. 1, the feed amount of oil by switching energization and (on) the non-conductive (off) Alternatively, either an on / off solenoid valve configured to control the discharge amount or a duty solenoid valve configured to control the supply amount or discharge amount of oil by controlling the ratio of the energization time may be used. Further, in the example shown in FIG. 3 to no example shown in FIG. 1, is configured so as to drive the oil pump by a power source 42 for generating a torque transmitted to the drive wheels, the torque transmitted to the drive wheels You may comprise so that the electric motor for exclusive use which drives an oil pump may be provided, without generating. Further, in the example shown in FIG. 3 to no example shown in FIG. 1, but the oil pump is shown as a hydraulic source for supplying oil to the hydraulic chambers, using an accumulator as a hydraulic pressure source, stored in the accumulator It is also possible to configure so that oil is supplied to each 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 pump

Claims (1)

Integral with the fixed piece flop Raimaripu Li is the rotation shaft of the primary pulley is constituted by the first movable piece is movable to the axis of rotation of the primary pulley so as to approach and away from the said fixing piece , constituting a cell Kandaripu Riga該secondary pulley fixed piece integral with the rotation shaft of the second movable piece is movable to the axis of rotation of the secondary pulley so as to approach and away from the said fixing piece by having the primary pulley and the bell preparative be found wrapped around the secondary pulley, the steplessly variable speed ratio by continuously changing the winding radius of the belt in the primary pulley and the secondary pulley in the hydraulic control apparatus is configured behenate belt type continuously variable transmission to change to,
It said first movable piece and the fixed piece in the primary pulley by pressing the first movable piece before Symbol from the oil pump is supplied oil in a direction along the rotation centric axis of the rotating shaft of the primary pulley before Symbol first squeezing pressure chamber Generating an clamping pressure sandwiching the belts between,
Wherein said fixed piece in the secondary pulley by pressing the put that before Symbol second movable piece before Symbol secondary pulley the oil is supplied in the direction along the rotation axis of the rotating during rotation central axis line of the secondary pulley before Symbol second squeezing pressure chamber Generating an clamping pressure sandwiching the belts between the second movable piece,
Before Symbol third movable piece movable in the direction along the rotation axis of the rotating during rotation central axis line of the previous SL secondary pulley in contact with the second movable piece,
By providing a thrust direction in which the OIL is along the rotation-centric axis of the rotating shaft before Symbol secondary pulley to the third movable piece is supplied, the shifting hydraulic chamber to change the gear ratio,
The first clamping hydraulic chamber and the second clamping hydraulic chamber are connected when the first clamping hydraulic chamber and the second clamping hydraulic chamber are connected and the speed ratio is changed. a connecting oil passage to traverse the oIL between,
Bei example and another oil passage supplying the oil to the shifting hydraulic chamber,
The speed change ratio can be changed by supplying the oil from the oil pump to the speed change hydraulic chamber through the other oil passage in a state where the oil supply from the oil pump to the connection oil passage is shut off. Composed and
From the maximum hydraulic pressure in the first clamping hydraulic chamber to be obtained from the maximum torque transmitted by the belt-type continuously variable transmission and to be applied to the first movable piece, and the maximum gear ratio in the belt-type continuously variable transmission The pressure receiving area of the first movable piece that receives the hydraulic pressure in the first clamping pressure hydraulic chamber so that the maximum hydraulic pressure in the shift hydraulic chamber to be obtained and applied to the third movable piece is the same; A pressure receiving area of the third movable piece that receives the hydraulic pressure of the shifting hydraulic chamber;
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 . A hydraulic control device for a belt-type continuously variable transmission.

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