JP6538090B2 - Continuously variable transmission - Google Patents

Description

  The present invention relates to a continuously variable transmission, and more particularly to a full toroidal continuously variable transmission.

  2. Description of the Related Art A full toroidal continuously variable transmission is known, in which a rotatably and tiltably supported roller is provided between an input disc to which a driving force is input and an output disc that outputs a driving force. (Patent Document 1). The continuously variable transmission disclosed in Patent Document 1 has a rotary shaft of a roller supported by a carriage, and is provided with a hydraulic cylinder that applies a driving force in the forward and backward directions of the carriage. Pressure oil is supplied from the two hydraulic pumps to the first and second oil chambers partitioned by the pistons of the hydraulic cylinders, and the carriage is advanced and retracted to rotate the rollers, thereby rotating the input and output disks. Change the speed ratio (gear ratio).

Japanese Patent Application Publication No. 2003-83409

  However, in the technique disclosed in Patent Document 1, since the hydraulic oil is supplied from the two hydraulic pumps to the first and second oil chambers respectively, a plurality of hydraulic devices for the two hydraulic pumps are required, and the hydraulic pressure is required. There is a problem that the circuit becomes complicated.

  The present invention has been made to solve the above-mentioned problems, and it is an object of the present invention to provide a continuously variable transmission which can simplify a hydraulic circuit.

Means for Solving the Problems and Effects of the Invention

In order to achieve this object, according to the continuously variable transmission of claim 1, it is provided between an input disk to which driving force is input, an output disk for outputting driving force, and an output disk and an input disk Hydraulic oil is supplied to a variator comprising a plurality of rollers. By utilizing the shear force of the oil film formed between the input disk and output disk and the rollers, the input disc, the driving force between the roller and the output disk is transmitted. The rotating shafts of the plurality of rollers are respectively supported by the plurality of carriages, and the driving force in the forward and backward directions with respect to the variator is respectively applied to the plurality of carriages by the plurality of hydraulic cylinders having the first and second oil chambers. A first oil passage and a second oil passage are connected to the first and second oil chambers, respectively, and a first hydraulic pump is connected to the first oil passage and the second oil passage. The pump drive drives the first hydraulic pump in the first direction and in the second direction opposite thereto, so that the first and second oil chambers pass from the one hydraulic pump through the first oil passage and the second oil passage. Can supply hydraulic oil to Therefore, there is an effect that the hydraulic circuit can be simplified.

A connection oil passage is connected to the third oil chamber, and an urging force for pinching the roller is applied to the input disc or the output disc by the third oil chamber. A first communication passage communicates with the first oil passage and the second oil passage, and a shuttle valve connected to the first communication passage and the connection oil passage connects the higher pressure of the first oil passage and the second oil passage. Lead to the oil path. Since the pressure oil can be supplied to the third oil chamber by using the pressure oil in the first oil passage and the second oil passage, compared to the case where a hydraulic pump for supplying the pressure oil to the third oil chamber is separately provided. The hydraulic circuit can be simplified.

When the first oil passage is at a lower pressure than the oil tank, the hydraulic oil in the oil tank is replenished from the first supplement passage to the first oil passage through the check valve. When the second oil passage is at a lower pressure than the oil tank, the hydraulic oil in the oil tank is replenished from the second supplement passage to the second oil passage through the check valve. As a result, it is possible to suppress a decrease in responsiveness due to hydraulic fluid leak (air biting).

The pressure of the connection oil passage detected by the pressure sensor coincides with the pressure on the high pressure side of the first oil passage and the second oil passage. Two pressure sensors are required to detect the pressure in the first oil passage and the second oil passage respectively, and one pressure sensor can be made by detecting the pressure in the connection oil passage, so one minute The cost of pressure sensors and wiring can be reduced.

Further, a pressure sensor is disposed in the connection oil passage, and the pressure detected by the pressure sensor is acquired by the pressure acquiring unit. Since the drive means drives the pump drive based on the pressure acquired by the pressure acquisition means, a closed loop is formed between the pressure sensor and the pump drive, and the pressure corresponding to the result of the drive force applied by the pump drive is returned. Feedback control can be performed. Therefore, there is an effect capable of improving the accuracy of pressure control. Further, since a necessary pressure can be obtained according to the driving force by feedback control, the number of pressure control valves and the like can be suppressed, and the energy loss for driving the first hydraulic pump can be suppressed.

  Since the hydraulic pump is controlled by the pressure sensor arranged in the connection oil passage, the number of parts can be reduced compared to the case where the hydraulic pump is controlled by the pressure sensors respectively arranged in the first oil passage and the second oil passage There is.

According to the continuously variable transmission according to claim 2, the switching valve disposed in the first oil passage and the second oil passage, the hydraulic oil from the first hydraulic pump to the first and second oil chambers A switch is made to allow or block the flow. When the transmission gear ratio is fixed, if the flow of hydraulic oil from the first hydraulic pump to the first and second oil chambers is blocked by the switching valve, pressure oil is not supplied from the first hydraulic pump. The pressure of the first and second oil chambers can also be maintained. Since the first hydraulic pump and the pump drive can be stopped during this time, in addition to the effects of claim 1, the energy loss for driving the first hydraulic pump and the pump drive and the heat generation due to the drive can be suppressed. .

According to the continuously variable transmission of the third aspect , the first hydraulic pump is driven in the first or second direction by the switching valve disposed in the first oil path and the second oil path. Alternatively, the introduction of the pressure into the second oil chamber and the simultaneous introduction of the pressure into the first and second oil chambers by driving the first hydraulic pump in the first or second direction are switched. By simultaneously introducing pressure into the first and second oil chambers by driving the first hydraulic pump in the first or second direction, in addition to the effect of claim 1 , the first and second oil chambers There is the effect that the pressure on the carriage and the roller can be in a predetermined initial position.

According to the continuously variable transmission of the fourth aspect , the switching valve disposed in the first oil passage and the second oil passage transfers hydraulic oil from the first hydraulic pump to the first and second oil chambers. A switch is made to allow or block the flow. When the transmission gear ratio is fixed, if the flow of hydraulic oil from the first hydraulic pump to the first and second oil chambers is blocked by the switching valve, pressure oil is not supplied from the first hydraulic pump. The pressure of the first and second oil chambers can also be maintained. Since the first hydraulic pump and the pump drive can be stopped during this time, in addition to the effects of claim 1, the energy loss for driving the first hydraulic pump and the pump drive and the heat generation due to the drive can be suppressed. .

Further, introduction of pressure to the first or second oil chamber by driving the first hydraulic pump in the first or second direction, and driving of the first hydraulic pump in the first or second direction The simultaneous introduction of the pressure into the first and second oil chambers by the. By simultaneously introducing pressure into the first and second oil chambers by driving the first hydraulic pump in the first or second direction, in addition to the effect of claim 1 , the first and second oil chambers There is the effect that the pressure on the carriage and the roller can be in a predetermined initial position.

According to the continuously variable transmission of claim 5 , the switching valve includes a valve drive that switches the flow passage communicating with the first oil passage and the second oil passage, so any one of claims 2 to 4 In addition to the effects of the above, there is an effect that switching of the switching valve can be automated as required.

According to the continuously variable transmission of the sixth aspect , the hydraulic fluid is supplied to the variator by the lubricating flow path. The second communication passage communicates with the first oil passage and the second oil passage, and the second direction control valve connected to the second communication passage and the lubricating oil passage is the higher of the first oil passage and the second oil passage. Lead pressure to the lubricating oil path. Since hydraulic oil can be supplied to the variator using the hydraulic oil in the first oil passage and the second oil passage, in addition to the effects of any of claims 1 to 5 , a hydraulic pump is additionally provided to supply the hydraulic oil to the variator. Compared to the case, there is an effect that the hydraulic circuit can be simplified.

According to the continuously variable transmission of the seventh aspect , the hydraulic fluid is supplied to the variator by the lubricating channel, and the second hydraulic pump operates to the lubricating oil channel having a lower pressure than the first oil channel and the second oil channel. Oil is supplied. The invention according to any one of claims 1 to 6 , by providing a second hydraulic pump for supplying hydraulic fluid to the lubricating oil passage separately from the first hydraulic pump for supplying hydraulic fluid to the first oil passage and the second oil passage. In addition, the size of the first hydraulic pump and the pump drive can be reduced as compared with the case where the second hydraulic pump is not provided. In addition, since the size of the first hydraulic pump and the pump drive can be reduced, the energy loss of the first hydraulic pump and the pump drive can be suppressed as compared with the case where the second hydraulic pump is not provided. .

According to the continuously variable transmission of the eighth aspect , hydraulic oil is supplied to the variator by the lubricating flow path. A piston rod to which the carriage is coupled is disposed in the first and second oil chambers, and an oil flow path forming a part of the lubricating oil path is formed inside the piston rod. The plurality of check valves communicate the oil passage with the first and second oil chambers, respectively, and the check valves prevent the flow of hydraulic fluid from the first and second oil chambers into the oil passage . Therefore, the hydraulic oil can be filled from the check valve into the first and second oil chambers by supplying the hydraulic oil from the oil flow path while removing air from the first and second oil chambers at the time of assembling the hydraulic cylinder. . Therefore, in addition to the effects of claims 1 to 7 , there is an effect that the assembling operation of the hydraulic cylinder can be facilitated. Also, when the hydraulic oil in the first and second oil chambers leaks during use, the hydraulic oil can be replenished from the check valve into the first and second oil chambers. Therefore, there is an effect that it is possible to suppress a decrease in responsiveness due to a leak of hydraulic oil (air biting).

FIG. 1 is a system diagram of a continuously variable transmission according to a first embodiment of the present invention. It is a systematic diagram of the continuously variable transmission in 2nd Embodiment. It is a systematic diagram of the continuously variable transmission in 3rd Embodiment. It is a systematic diagram of the continuously variable transmission in 4th Embodiment. It is a systematic diagram of the continuously variable transmission in 5th Embodiment. It is a systematic diagram of the continuously variable transmission in 6th Embodiment. It is a systematic diagram of the continuously variable transmission in 7th Embodiment. It is a systematic diagram of the continuously variable transmission in 8th Embodiment.

  Hereinafter, preferred embodiments of the present invention will be described with reference to the attached drawings. First, a continuously variable transmission 10 according to a first embodiment of the present invention will be described with reference to FIG. FIG. 1 is a system diagram of a continuously variable transmission 10 according to a first embodiment of the present invention. Although continuously variable transmission 10 is provided with a plurality of variators 11 each having a plurality of rollers 16, in FIG. 1, one variator 11 and one roller 16 are illustrated for simplification (FIG. 2 to FIG. The same in 8).

  As shown in FIG. 1, the continuously variable transmission 10 is for outputting the driving force (torque) from the driving source (engine) mounted on the vehicle to the driving wheel side under the optimal condition according to the traveling state of the vehicle. This is a full toroidal type transmission that can control the transmission ratio steplessly (continuously). The continuously variable transmission 10 includes a variator 11, a hydraulic cylinder 20, and a hydraulic pump 33 (first hydraulic pump) for supplying pressure oil to the hydraulic cylinder 20. In the continuously variable transmission 10, each part of the continuously variable transmission 10 is controlled by an ECU 50 (Electronic Control Unit).

  The variator 11 is provided with an input disk 12, an output disk 13 and a roller 16, and is driven using a shear force of an oil film of hydraulic oil (lubricating oil) formed between the input disk 12 and the output disk 13 and the roller 16. Transmit the power. The input disk 12 is a member to which driving force from the engine side is input, and has a toroidal surface. The output disk 13 is a member that outputs the driving force to the drive wheel (not shown) side, and has a toroidal surface facing the toroidal surface of the input disk 12. An oil chamber 15 (third oil chamber) is formed between the output disk 13 and the piston 14 disposed on the rear side. The roller 16 is a member in which a curved surface corresponding to a toroidal surface is formed on the outer peripheral surface, and is sandwiched between the input disk 12 and the output disk 13. The roller 16 is rotatably provided on the carriage 17 coupled to the piston rod 21 of the hydraulic cylinder 20 by the rotation shaft 18 and rotatable about the axis of the piston rod 21.

  The hydraulic cylinder 20 is a double-acting type device for applying a driving force in the forward and backward directions to the input disk 12 and the output disk 13 to the carriage 17, and the first oil chamber 23 is fixed by the piston 22 fixed to the piston rod 21. And the second oil chamber 24 are partitioned. In the continuously variable transmission 10, when the driving force is transmitted between the input disc 12 and the output disc 13 via the roller 16, the reaction force acting on the roller 16 and the drive disc necessary for driving the output disc 13 When an imbalance occurs with the driving force, the roller 16 automatically changes its angle to eliminate this imbalance. For example, if a force is generated that pushes or pulls the roller 16 against the oil pressure in the oil chambers 23 and 24 due to fluctuations in the traveling load or adjustment of the accelerator pedal, the angle of the roller 16 changes and the input disc 12 The transmission gear ratio, which is the rotational speed ratio of the output disc 13 to the output disc 13, is changed. That is, the hydraulic cylinder 20 moves the roller 16 together with the carriage 17 according to the hydraulic pressure of the oil chambers 23 and 24 and changes the gear ratio by tilting the roller 16 with respect to the input disk 12 and the output disk 13.

  The hydraulic circuit 30 includes a first oil passage 31, a second oil passage 32 and a hydraulic pump 33. The first oil passage 31 is a hydraulic pipe connected to the oil chamber 23, and the second oil passage 32 is a hydraulic pipe connected to the oil chamber 24. A hydraulic pump 33 (first hydraulic pump) is connected to the first oil passage 31 and the second oil passage 32. The hydraulic pump 33 is rotationally driven by a motor 34 (pump drive device).

  The motor 34 is a device that can be rotationally driven in a first direction and a second direction opposite thereto, and is connected to the ECU 50. The ECU 50 performs control to rotationally drive the motor 34 in the first direction or the second direction, and the hydraulic pump 33 accordingly rotates in the first direction or the second direction.

  The first oil passage 31 and the second oil passage 32 are connected to a first communication passage 35 communicating with each other. The first communication passage 35 is provided with a shuttle valve 36 (first direction control valve), and the hydraulic oil supplied to the first oil passage 31 and the second oil passage 32 is shuttled from the first communication passage 35. The valve 36 is input. Since the oil chamber 15 is connected to the output side via the connection oil passage 37, the shuttle valve 36 outputs the pressure oil on the high pressure side of the first oil passage 31 and the second oil passage 32 to the oil chamber 15. And prevents the flow of hydraulic oil from the oil chamber 15 to the low pressure side of the first oil passage 31 and the second oil passage 32.

  The oil tank 40 is for storing the hydraulic oil flowing through the hydraulic circuit 30, and the recovery path 41 connected to the variator 11 is connected. The recovery path 41 is a pipe for recovering the hydraulic oil (lubricating oil) supplied to the variator 11 mainly from a lubricating oil path (not shown) into the oil tank 40. An oil film is formed between the input disk 12 and the output disk 13 and the roller 16 by the hydraulic oil (lubricating oil) supplied to the variator 11. The variator 11 transmits the driving force by using the shear force of the oil film.

  The oil tank 40 can be provided for the continuously variable transmission 10 as a dedicated item. In addition, oil chambers of other power transmission devices mounted on a vehicle can also be used. The oil tank 40 is provided with a first supplement passage 42 and a second supplement passage 44 respectively communicating with the first oil passage 31 and the second oil passage 32. In the first refill passage 42 and the second refill passage 44, check valves 43 and 45 are disposed, respectively. The check valves 43 and 45 are valves for blocking the flow of hydraulic oil from the first oil passage 31 or the second oil passage 32 to the oil tank 40.

  The first oil passage 31 and the second oil passage 32 are provided with pressure sensors 51 and 52 (first and second pressure sensors), respectively. The pressure sensors 51 and 52 each include a detection unit (not shown) that detects a pressure, and an output circuit (not shown) that processes the detection result and outputs the processed result to the ECU 50.

  When pushing out the roller 16 with respect to the input disk 12 and the output disk 13, the ECU 50 controls the motor 34 to rotate it in the first direction, and the hydraulic oil pressurized by the hydraulic pump 33 from the first oil passage 31. The fluid is discharged to the oil chamber 23, and the working oil of the oil chamber 24 is sucked from the second oil passage 32. The ECU 50 controls the motor 34 to rotate the motor 16 in a second direction opposite to the first direction when drawing out the roller 16 with respect to the input disk 12 and the output disk 13, and the hydraulic oil pressurized by the hydraulic pump 33 Is discharged from the second oil passage 32 to the oil chamber 24 and the working oil of the oil chamber 23 is sucked from the first oil passage 31. The continuously variable transmission 10 can supply hydraulic oil from one hydraulic pump 33 to the oil chambers 23 and 24 through the first oil passage 31 and the second oil passage 32. Therefore, the number of hydraulic devices such as the hydraulic pump and the pressure control valve And the hydraulic circuit 30 can be simplified.

  The continuously variable transmission 10 guides the higher pressure of the first oil passage 31 and the second oil passage 32 from the first communication passage 35, the shuttle valve 36 and the connection oil passage 37 to the oil chamber 15, and the output disc 13 Is pressed to the input disk 12 side, and the roller 16 is pressed against the input disk 12 and the output disk 13. The continuously variable transmission 10 can supply pressure oil to the oil chamber 15 by using the pressure oil in the first oil passage 31 and the second oil passage 32. Therefore, a hydraulic pump for supplying pressure oil to the oil chamber 15 is separately provided. The hydraulic circuit 30 can be simplified as compared to the case. Further, the leakage of hydraulic oil from the oil chamber 15 and the connection oil passage 37 can be compensated from the first oil passage 31 and the second oil passage 32 by the shuttle valve 36.

  The pressures of the first oil passage 31 and the second oil passage 32 are respectively detected by the pressure sensors 51 and 52, and the ECU 50 drives the motor 34 based on the detected pressure. Therefore, it is possible to form a closed loop between the pressure sensors 51 and 52, the ECU 50 and the motor 34, and to perform feedback control for returning the pressure corresponding to the result of the driving force applied to the hydraulic pump 33 by the motor 34. Therefore, the accuracy of pressure control, that is, the accuracy of control of the tilt angle of the roller 16 can be improved.

  In the conventional continuously variable transmission, although the pressure oil is supplied to the oil chambers 31 and 32 by controlling the flow control valve disposed in the hydraulic circuit 30, when the required torque is low, that is, in the oil chambers 23 and 24 Even when the required pressure is low, the pressures of the first oil passage 31 and the second oil passage 32 need to be maintained higher than the required pressure. Therefore, the difference between the set pressure of the hydraulic pump for making the first oil passage 31 and the second oil passage 32 high and the necessary pressure results in the loss of drive energy of the hydraulic pump. Further, since the required pressure of the oil chambers 23 and 24 is adjusted by feed forward control of the flow control valve, there is a problem that the accuracy of pressure control, that is, the accuracy of control of the tilt angle of the roller 16 is low.

  On the other hand, according to the present embodiment, since the required pressure can be obtained according to the required torque by feedback control, the flow control valve can be made unnecessary and energy loss of the motor 34 for driving the hydraulic pump 33 can be suppressed. it can.

  When a leak occurs in the hydraulic circuit 30 and it is necessary to supplement the hydraulic oil from the oil tank 40, the ECU 50 drives the motor 34 to operate the hydraulic pump 33. When the hydraulic fluid in the first oil passage 31 and the oil chamber 23 is sucked by the hydraulic pump 33 and the first oil passage 31 becomes lower in pressure than the oil tank 40, the hydraulic oil in the oil tank 40 reverses from the first refill passage 42. The first oil passage 31 is compensated through the stop valve 43. Similarly, when the hydraulic oil in the second oil passage 32 and the oil chamber 24 is sucked by the hydraulic pump 33 and the pressure in the second oil passage 32 becomes lower than that of the oil tank 40, the hydraulic oil in the oil tank 40 becomes the second refill passage. From 44 to the second oil passage 32 via the check valve 46 is compensated. As a result, it is possible to suppress a decrease in responsiveness due to hydraulic fluid leak (air biting).

  Next, a second embodiment will be described with reference to FIG. In the first embodiment, the case where the pressure sensors 51 and 52 are provided in the first oil passage 31 and the second oil passage 32 has been described. On the other hand, in the second embodiment, the case where the pressure sensor 111 is provided in the connection oil passage 37 instead of the first oil passage 31 and the second oil passage 32 will be described. In addition, about the part same as the part demonstrated in 1st Embodiment, the same code | symbol is attached | subjected and the following description is abbreviate | omitted. FIG. 2 is a system diagram of continuously variable transmission 110 according to the second embodiment. The continuously variable transmission 110 includes a pressure sensor 111 disposed in the connection oil passage 37.

  The pressure sensor 111 includes a detection unit (not shown) for detecting pressure, and an output circuit (not shown) for processing the detection result and outputting the result to the ECU 50, and is disposed in the connection oil passage 37 . The pressure in the connection oil passage 37 detected by the pressure sensor 111 matches the pressure on the high pressure side in the first oil passage 31 and the second oil passage 32. When detecting the pressure of the first oil passage 31 and the second oil passage 32, respectively, two pressure sensors 51 and 52 are required. By detecting the pressure of the connection oil passage 37, one pressure sensor 111 is provided. Therefore, the cost of one pressure sensor and wiring between the pressure sensor and the ECU 50 can be reduced.

  Next, a third embodiment will be described with reference to FIG. In the third embodiment, a continuously variable transmission 210 including a switching valve 211 that shuts off the first oil passage 31 and the second oil passage 32 will be described. In addition, about the part same as the part demonstrated in 1st and 2nd embodiment, the same code | symbol is attached | subjected and the following description is abbreviate | omitted. FIG. 3 is a system diagram of the continuously variable transmission 210 according to the third embodiment.

  The switching valve 211 is an electromagnetic valve that is driven by energizing a solenoid 212 (valve drive device), and is connected to the ECU 50. The ECU 50 controls the driving of the switching valve 211. In the switching valve 211, the flow path is opened by the biasing force of the elastic member 213 when the solenoid 212 is not energized, and the hydraulic pump 33 is connected to the oil chambers 23 and 24. In the switching valve 211, when the valve body moves against the biasing force of the elastic member 213 when the solenoid 212 is energized, the flow path is closed, and the connection between the hydraulic pump 33 and the oil chambers 23, 24 is cut off.

  When the transmission gear ratio is fixed, the ECU 50 energizes the solenoid 212 to close the flow path by the switching valve 211, thereby blocking the flow of hydraulic fluid from the hydraulic pump 33 to the oil chambers 23 and 24. Next, the ECU 50 stops the motor 34 to stop the supply of pressure oil by the hydraulic pump 33. Since the first oil passage 31 and the second oil passage 32 are closed by the switching valve 211, the pressure of the oil chambers 23, 24 can be maintained without driving the motor 34 and supplying the pressure oil from the hydraulic pump 33. Since the motor 34 and the hydraulic pump 33 can be stopped while the pressure in the oil chambers 23 and 24 can be maintained, energy loss for driving the motor 34 and the hydraulic pump 33 and heat generation due to their driving can be suppressed. Further, since the switching valve 211 simultaneously opens or closes the flow paths respectively communicating with the first oil path 31 and the second oil path 32 by the solenoid 212, switching of the switching valve 211 can be automated as required.

  Next, a fourth embodiment will be described with reference to FIG. In the fourth embodiment, a continuously variable transmission 310 provided with a switching valve 311 disposed in the first oil passage 31 and the second oil passage 32 will be described. In addition, about the part same as the part demonstrated in 1st and 2nd embodiment, the same code | symbol is attached | subjected and the following description is abbreviate | omitted. FIG. 4 is a system diagram of continuously variable transmission 310 according to the fourth embodiment.

  The switching valve 311 is an electromagnetic valve that is driven by energizing a solenoid 312 (valve drive device), and is connected to the ECU 50. The ECU 50 controls the driving of the switching valve 311. The flow path of the switching valve 311 is opened by the biasing force of the elastic member 313 when the solenoid 312 is not energized, and the hydraulic pump 33 is connected to the oil chambers 23 and 24 as in the second embodiment.

  The ECU 50 energizes the solenoid 312 when the carriage 21 and the roller 16 are in the initial position. The flow path of the switching valve 311 is switched by the valve body moving against the biasing force of the elastic member 313 by the solenoid 312. After switching the flow path of the switching valve 311, when the motor 34 is rotated in the first direction, one port of the motor 34 passes through the first oil passage 31 and the second oil passage 32 to the oil chambers 23, 24 as well. Pressure can be introduced simultaneously. Since the pressures of the oil chambers 23 and 24 can be balanced, the carriage 21 and the roller 16 can be in the initial position. At this time, the switching valve 311 collects drain from the other port of the motor 34. Further, since the switching valve 311 switches the flow passage communicating with the first oil passage 31 and the second oil passage 32 by the solenoid 312, switching of the switching valve 311 can be automated as required.

  Next, a fifth embodiment will be described with reference to FIG. In the fifth embodiment, a continuously variable transmission 410 provided with a switching valve 411 disposed in the first oil passage 31 and the second oil passage 32 will be described. In addition, about the part same as the part demonstrated in 1st and 2nd embodiment, the same code | symbol is attached | subjected and the following description is abbreviate | omitted. FIG. 5 is a system diagram of a continuously variable transmission 410 according to the fifth embodiment.

  The switching valve 411 is an electromagnetic valve driven by energizing the solenoids 412 and 413 (valve drive device), and is connected to the ECU 50. The ECU 50 controls the driving of the switching valve 411. The switching valve 411 switches the position of the valve to any of the following three by energizing the solenoids 412 and 413. From the left in FIG. 5, (1) one port of the motor 34 is communicated with the first oil passage 31 and the second oil passage 32 and drains are collected from the other port of the motor 34 (2) of the hydraulic pump 33 (3) prevent communication between both ports of the hydraulic pump 33 and the first oil passage 31 and the second oil passage 32. position.

  In the position (1), the pressures in the oil chambers 23 and 24 can be balanced, and the carriage 21 and the roller 16 can be set to predetermined initial positions. At the position (2), the flow path of the switching valve 411 is opened, and the hydraulic pump 33 is connected to the oil chambers 23 and 24 as in the second embodiment. In the position (3), the pressure in the oil chambers 23 and 24 can be maintained without supplying the pressure oil from the hydraulic pump 33. Since the switching valve 411 switches the flow passage communicating with the first oil passage 31 and the second oil passage 32 by the solenoids 412 and 413, switching of the switching valve 411 can be automated as required.

  A sixth embodiment will now be described with reference to FIG. In the sixth embodiment, a case will be described where a lubricating oil passage 513 for supplying lubricating oil (hydraulic oil) to the variator 11 using the pressure difference between the first oil passage 31 and the second oil passage 32 is provided. In addition, about the part same as the part demonstrated in 1st Embodiment, the same code | symbol is attached | subjected and the following description is abbreviate | omitted. FIG. 6 is a system diagram of continuously variable transmission 510 according to the sixth embodiment.

  In the continuously variable transmission 510, a second communication passage 511 which connects the first oil passage 31 and the second oil passage 32 to each other is connected to the first oil passage 31 and the second oil passage 32. The second communication passage 511 is provided with a shuttle valve 512 (second direction control valve), and the hydraulic oil supplied to the first oil passage 31 and the second oil passage 32 is shuttled from the second communication passage 511. It is input to the valve 512. The shuttle valve 512 has the variator 11 connected to the output side via the lubricating oil passage 513. Since the pressure reducing valve 514 is disposed in the lubricating oil passage 513, the pressure oil on the high pressure side in the first oil passage 31 and the second oil passage 32 is reduced in pressure by the pressure reducing valve 514 and output to the variator 11. The shuttle valve 512 blocks the flow of hydraulic oil from the oil chamber 15 to the low pressure side of the first oil passage 31 and the second oil passage 32.

  The hydraulic oil (lubricating oil) supplied from the lubricating oil passage 513 to the variator 11 is supplied between the input disc 12 and the output disc 13 and the roller 16 and is used to form an oil film. The variator 11 transmits the driving force by using the shear force of the oil film. The continuously variable transmission 510 can supply hydraulic oil (lubricating oil) to the variator 11 using the hydraulic oil in the first oil passage 31 and the second oil passage 32. Therefore, a hydraulic pump for supplying the hydraulic oil to the variator 11 is used. The hydraulic circuit can be simplified as compared to the case of providing separately. Since the lubricating oil passage 513 is depressurized by the pressure reducing valve 514, the oil amount (hydraulic pressure) necessary for forming an oil film can be supplied from the first oil passage 31 and the second oil passage 32 to the variator 11. Further, the leakage of the hydraulic oil from the variator 11 can be compensated from the first oil passage 31 and the second oil passage 32 by the shuttle valve 512.

  A seventh embodiment will now be described with reference to FIG. In the sixth embodiment, the second communication passage 511, the shuttle valve 512 and the lubricating oil passage 513 are provided, and the operating oil (lubricating oil) is supplied to the variator 11 using the pressure of the first oil passage 31 and the second oil passage 32. The case of supply has been described. On the other hand, in the seventh embodiment, the case where the lubricating oil passage 611 is provided separately from the first oil passage 31 and the second oil passage 32 will be described. In addition, about the part same as the part demonstrated in 1st Embodiment, the same code | symbol is attached | subjected and the following description is abbreviate | omitted. FIG. 7 is a system diagram of continuously variable transmission 610 according to the seventh embodiment.

  The continuously variable transmission 610 is provided with a lubricating oil passage 611 for supplying a working oil (lubricating oil) to the variator 11. The lubricating oil passage 611 is connected at a first end to the variator 11 and at a second end to the oil tank 40. The lubricating oil passage 611 is provided with a hydraulic pump 612 (second hydraulic pump). The hydraulic pump 612 is rotationally driven by an engine 613 (pump drive device). The hydraulic oil supplied from the oil tank 40 to the variator 11 through the lubricating oil passage 611 is recovered to the oil tank 40 through the recovery passage 41.

  The lubricating oil passage 611 is set to a low pressure as compared with the first oil passage 31 and the second oil passage 32. Compared with the case where the hydraulic pump 612 is not provided by providing the hydraulic pump 612 for supplying the hydraulic fluid to the lubricating oil passage 611 separately from the hydraulic pump 33 for supplying the hydraulic fluid to the first oil passage 31 and the second oil passage 32 Thus, the size and capacity of the hydraulic pump 33 and the motor 34 can be reduced. Since the sizes and capacities of the hydraulic pump 33 and the motor 34 can be reduced, energy loss of the hydraulic pump 33 and the motor 34 can be suppressed as compared with the case where the hydraulic pump 612 is not provided.

  Next, an eighth embodiment will be described with reference to FIG. In the first to seventh embodiments, the check valves 43 and 45 are respectively provided in the first supplement passage 42 and the second supplement passage 44 respectively communicating with the first oil passage 31 and the second oil passage 32, The case where the leak of hydraulic fluid from the first oil passage 31, the second oil passage 32, and the oil chambers 23, 24 is compensated from the first refill passage 42 and the second refill passage 44 has been described. On the other hand, in the eighth embodiment, the check valves 721 and 722 are provided between the oil chambers 23 and 24 of the hydraulic cylinder 711 and the oil flow passage 713 respectively, and the first oil passage 31 and the second oil passage 32 The case where the leakage of the hydraulic oil from the oil chambers 23 and 24 is compensated from the oil flow path 713 will be described. The same parts as the parts described in the first to seventh embodiments will be assigned the same reference numerals and explanation thereof will be omitted. FIG. 8 is a system diagram of continuously variable transmission 710 in the eighth embodiment.

  The continuously variable transmission 710 is provided with a hydraulic cylinder 711. In the hydraulic cylinder 711, a piston rod 712 to which the carriage 17 is fixed is formed to pass through the oil chambers 23 and 24. The piston rod 712 is formed with an oil flow passage 713 penetrating in the longitudinal direction. The piston 714 is centrally formed with a through hole penetrating in the thickness direction, and is fixed to the central outer peripheral surface in the longitudinal direction of the piston rod 712 by inserting the piston rod 712 through the through hole. The oil chambers 23, 24 are defined by the piston 714. The movement of the piston rod 712 together with the piston 714 in accordance with the hydraulic pressure of the oil chambers 23 and 24 causes the roller 16 to move back and forth relative to the variator 11.

  The hydraulic cylinder 711 is provided with check valves 721 and 722 on both sides of the piston 714 in the longitudinal direction of the piston rod 714. The check valves 721 and 722 are valves that communicate the oil chambers 23 and 24 with the oil flow path 713, and allow the hydraulic oil to flow from the oil flow path 713 to the oil chambers 23 and 24, 24 prevents the flow of hydraulic oil from the oil passage 24 to the oil passage 713.

  The lubricating oil passage 715 is connected to an oil passage 713 formed in the piston rod 712, and the hydraulic motor 612 sucks and pressurizes the hydraulic oil of the oil tank 40 and supplies it to the oil passage 713. The hydraulic oil (lubricating oil) supplied to the oil flow path 713 travels along the carriage 17 and reaches the rotation shaft 18 of the roller 16. The hydraulic oil reaching the rotation shaft 18 (center of the roller 16) flows to the outer peripheral surface of the roller 16 while cooling the side surface of the roller 16, and between the input disk 12 and the output disk 13 and the roller 16 (a part where traction occurs) Cool the part where traction occurs while forming an oil film). The hydraulic oil (lubricating oil) deprives the heat generated by the traction between the input disk 12 and the output disk 13 and the roller 16, so that the viscosity of the oil film is prevented from decreasing and the oil film can be prevented from running out. By increasing the cooling efficiency of the roller 16 by the hydraulic oil to prevent the oil film from being exhausted, it is possible to obtain a high transmission torque that causes the traction accompanied by a large temperature rise.

  Since continuously variable transmission 710 is configured as described above, at the time of assembly of hydraulic cylinder 711, check valves 721 and 722 are taken out of oil flow path 713 and oil chambers 23 and 24 while removing air from oil chambers 23 and 24. By supplying the hydraulic oil to the oil chamber 23, the oil chambers 23, 24 can be filled with the hydraulic oil. Therefore, the assembly operation of the hydraulic cylinder 711 can be facilitated. In addition, when the hydraulic oil in the oil chambers 23 and 24 leaks during use, the pressure in the oil passage 713 is higher than that in the oil chambers 23 and 24 so that the check valves 721 and 722 operate to the oil chambers 23 and 24. Oil can be replenished. As a result, it is possible to suppress a decrease in responsiveness due to hydraulic fluid leak (air biting).

  Although the present invention has been described above based on the embodiment, the present invention is not limited to the above embodiment, and various improvements and modifications can be made without departing from the scope of the present invention. It can be easily guessed.

  In each of the above embodiments, the oil chamber 15 is provided on the output disk 13 side of the variator 11, and the piston 14 presses the output disk 13 toward the input disk 12 to hold the roller 16; It is not limited. On the contrary, it is naturally possible to provide the oil chamber 15 on the input disc 12 side and press the input disc 12 to the output disc 13 side.

  In the above embodiments, the case where the pressure on the high pressure side of the first oil passage 31 and the second oil passage 32 and the pressure of the oil chamber 15 are made to be the same by the connection oil passage 37 has been described. It is not a thing. Instead of the connection oil passage 37, it is naturally possible to provide a hydraulic circuit communicating with the oil chamber 15 and pressurize the oil chamber 15 with a hydraulic pump disposed in the hydraulic circuit.

  In each of the above embodiments, the shuttle valves 36 and 512 are used as the direction control valves, but the present invention is not necessarily limited thereto. Instead of the shuttle valves, other direction control valves such as electromagnetic switching valves may be used. Of course it is possible to use. In that case, the ECU 50 controls the electromagnetic switching valve in conjunction with the control of the motor 34, and supplies the pressure oil of the first oil passage 31 or the second oil passage 32 to the oil chamber 15.

  In the seventh and eighth embodiments, the hydraulic pump 612 disposed in the lubricating oil passages 611 and 715 is driven by the engine 613. However, the present invention is not necessarily limited thereto, and is separately provided. It is of course possible to drive the hydraulic pump 612 by means of a motor.

  In the third embodiment, the case where the switching valve 211 for opening the flow path when not energized and closing the flow path when energized is provided. However, the present invention is not necessarily limited thereto. Naturally, it is possible to use a switching valve 211 that closes and opens the flow path at the time of energization. Similarly, in the fourth embodiment, there is described the case where the switching valve 311 is provided which opens the flow passage at the time of non-energization and simultaneously pressurizes the first oil passage 31 and the second oil passage 32 at the time of electricity application. Naturally, it is possible to use the switching valve 311 which simultaneously pressurizes the first oil passage 31 and the second oil passage 32 at the time of non-energization and opens the passage at the time of electricity application.

  In the above-described first to seventh embodiments, the first refill passage 42 and the second refill passage 44 respectively communicating with the first oil passage 31 and the second oil passage 32 are provided. The case where the hydraulic oil is refilled from the oil tank 40 to the hydraulic circuit 30 using the 2 refilling path 44 has been described. However, it is of course possible to omit the first filling passage 42 and the second filling passage 44.

10, 110, 210, 310, 410, 510, 610, 710 continuously variable transmission 11 variator 12 input disc 13 output disc 15 oil chamber (third oil chamber)
16 roller 17 carriage 18 rotary shaft 20, 711 hydraulic cylinder 23 oil chamber (first oil chamber)
24 oil chamber (second oil chamber)
31 first oil passage 32 second oil passage 33 hydraulic pump (first hydraulic pump)
34 Motor (Pump Drive Unit)
35 first communication passage 36 shuttle valve 37 connected oil passage
40 oil tank
42 first replenishment path
43 check valve
44 second replenishment path
45 check valve 50 ECU (pressure acquisition means, drive means)
111 Pressure sensor 211, 311, 411 Switching valve 212, 312, 412, 413 Solenoid (valve drive device)
511 second communication passage 512 shuttle valve (second direction control valve)
513,611,715 Lubricating oil path 612 hydraulic pump (second hydraulic pump)
712 piston rod 713 oil flow path 721, 722 check valve

Claims (8)

A variator including an input disk to which a driving force is input, an output disk for outputting the driving force, and a plurality of rollers provided between the output disk and the input disk;
A plurality of carriages respectively supporting rotation shafts of the plurality of rollers;
A plurality of hydraulic cylinders each having a first and a second oil chamber for applying a driving force in the direction of movement to and from the variator to the plurality of carriages,
First and second oil passages respectively connected to the first and second oil chambers;
A first hydraulic pump connected to the first oil passage and the second oil passage;
A pump drive which drives the first hydraulic pump in a first direction and a second direction opposite thereto, and supplies hydraulic fluid to the first oil passage and the second oil passage ;
A first refill passage connecting an oil tank and the first oil passage;
A second filling passage communicating the oil tank with the second oil passage;
A check valve disposed in each of the first refill passage and the second refill passage, for blocking the flow of hydraulic oil from the first oil passage and the second oil passage to the oil tank;
A third oil chamber for applying an urging force for clamping the roller to the input disc or the output disc;
A connected oil passage connected to the third oil chamber;
First communication passages respectively communicating with the first oil passage and the second oil passage;
A shuttle valve connected to the first communication passage and the connection oil passage to lead the higher pressure of the first oil passage and the second oil passage to the connection oil passage;
A pressure sensor disposed in the connection oil passage;
Pressure acquisition means for acquiring the pressure detected by the pressure sensor;
And a driving means for driving the pump driving device based on the pressure acquired by the pressure acquiring means . A switch disposed between the first oil passage and the second oil passage and switching between permitting or blocking the flow of hydraulic fluid from the first hydraulic pump to the first and second oil chambers continuously variable transmission of claim 1 Symbol mounting, characterized in that it comprises a valve. It is disposed in the first oil passage and the second oil passage, and is driven to the first or second oil chamber by driving the first hydraulic pump in the first or second direction. It has a switching valve for switching between introduction of pressure and simultaneous introduction of pressure into the first and second oil chambers by driving the first hydraulic pump in the first or second direction. and continuously variable transmission according to claim 1 Symbol mounting, characterized in that are. Switching between permitting or blocking the flow of hydraulic fluid from the first hydraulic pump to the first and second oil chambers while being disposed in the first oil passage and the second oil passage; Introduction of pressure to the first or second oil chamber by driving the first hydraulic pump in the first or second direction, and the first or the second of the first hydraulic pump wherein by driving the second direction the first and continuously variable transmission according to claim 1 Symbol mounting, characterized in that it comprises a switching valve for switching the simultaneous introduction of pressure to the second oil chamber. 5. The continuously variable transmission according to any one of claims 2 to 4 , wherein the switching valve includes a valve drive unit that switches a flow path communicating with the first oil path and the second oil path. . A lubricating oil passage for supplying hydraulic oil to the variator;
A second communication passage respectively communicating with the first oil passage and the second oil passage;
And a second directional control valve connected to the second communication passage and the lubricating oil passage, for guiding the higher pressure of the first oil passage and the second oil passage to the lubricating oil passage. The continuously variable transmission according to any one of claims 1 to 5 , characterized in that: A lubricating oil passage for supplying hydraulic oil to the variator;
7. A hydraulic pump according to any one of claims 1 to 6 , further comprising a second hydraulic pump for supplying hydraulic oil to the lubricating oil passage having a pressure lower than that of the first oil passage and the second oil passage. Continuously variable transmission. A lubricating oil passage for supplying hydraulic oil to the variator;
A piston rod disposed in the first and second oil chambers and to which the carriage is coupled;
An oil passage formed inside the piston rod and forming a part of the lubricating oil passage;
A plurality of check valves are provided that communicate the oil flow path with the first and second oil chambers, respectively, and prevent the flow of hydraulic oil from the first and second oil chambers to the oil flow path. The continuously variable transmission according to any one of claims 1 to 7 , wherein the continuously variable transmission is provided.

Images