JP4124765B2 - Hydraulic supply device - Google Patents

Description

  The present invention relates to a hydraulic pressure supply device that is used in a hybrid vehicle or the like and supplies hydraulic oil to a transmission mechanism or the like by an electric oil pump when the engine is stopped.

  In order to improve environmental efficiency by improving fuel consumption and reducing exhaust gas, hybrid vehicles that can be driven by a drive source that combines an engine and a motor that can generate electric power (motor generator) have been developed. This hybrid vehicle performs so-called idle stop control in which the engine is stopped when the vehicle is stopped. However, when the engine stops, the mechanical oil pump that supplies hydraulic oil to the transmission mechanism and the like is also stopped by the engine. An electric oil pump that is driven by an electric motor driven by a battery and supplies hydraulic oil only when the operation is performed is provided (for example, see Patent Document 1).

JP 2003-307271 A

  Since this electric oil pump operates while the engine is stopped by idle stop control, if air bubbles enter the hydraulic circuit while the engine is starting, that is, the electric oil pump is stopped, By sucking in the bubbles, a momentary idling occurs and a large load fluctuation is given to the electric motor.

  A sensorless brushless motor may be used as an electric motor for driving the electric oil pump. However, when the sensorless brushless motor is subjected to a large load fluctuation as described above, there is a possibility of inducing unstable operation. .

  The present invention has been made in view of such a problem, and has an electric oil pump. When an electric motor that drives the electric oil pump is started, a constant rotation control is performed to rotate the motor at a predetermined speed. It is an object of the present invention to provide a hydraulic pressure supply device in which torque control is performed so that the torque is output.

The hydraulic pressure supply device according to the present invention includes a drive source for driving a vehicle, a mechanical oil pump driven by the drive source, an electric motor driven by a battery, and an electric oil driven by the electric motor. A speed change mechanism that sets a speed change ratio by hydraulic oil supplied from a pump, a mechanical oil pump and an electric oil pump, shifts a rotational driving force of a drive source and transmits it to a wheel, and an operation discharged by an electric oil pump The oil pressure sensor detects the oil pressure of the oil and a pump driver that controls the operation of the electric motor. When the pump driver starts the electric motor, the fluctuation amount of the oil pressure exceeds a predetermined value. When the electric motor is operated so that the predetermined number of rotations is achieved, the electric torque is output so that the predetermined torque is output when the fluctuation amount becomes smaller than the predetermined value. Configured to actuate the over data.

The hydraulic pressure supply device according to the present invention preferably includes an oil temperature sensor that detects the oil temperature of the hydraulic oil, and the pump driver is configured to set the rotational speed in accordance with the oil temperature.

Further, such a hydraulic pressure supply device according to the present invention is provided in an oil passage (for example, the fifth oil passage 37 in the embodiment) that connects the discharge side and the suction side of the electric oil pump, and is provided in the oil passage. It is preferable to have a relief valve that is opened when the hydraulic pressure on the side exceeds a predetermined value.

  At this time, it is preferable that the hydraulic pressure at which the relief valve is opened is set to a value smaller than the hydraulic pressure at which the electric oil pump supplies hydraulic oil to the transmission mechanism.

Further, when the hydraulic pressure supply device according to the present invention is configured as described above, when the bubbles are sucked into the electric oil pump and the discharged hydraulic pressure fluctuates (pulsates), the bubbles are maintained at a constant rotational speed. Therefore, the electric motor can be stably operated when shifting to an operation in which a predetermined torque is output. At this time, by setting the number of rotations that is kept constant according to the oil temperature, it is possible to more reliably disperse the bubbles and to stably operate the electric motor.

  In addition, by providing a circulation circuit consisting of an oil passage connecting the discharge side and the suction side of the electric oil pump and a relief valve, the hydraulic oil discharged from the electric oil pump circulates through this recirculation circuit, so that a predetermined torque is generated. The electric motor can be stably operated in the output operation. In particular, when the pressure at which the relief valve is opened is set to a value smaller than the pressure at which the electric oil pump supplies hydraulic oil to the transmission mechanism, the effect is further exhibited.

  Hereinafter, preferred embodiments of the present invention will be described with reference to the drawings. First, the configuration of a traveling drive system of a hybrid vehicle having a hydraulic pressure supply device according to the present invention will be described with reference to FIG.

  The hybrid vehicle 1 has an engine 2 and a motor (hereinafter referred to as “motor generator”) 4 that are connected in series as a drive source, and a lockup clutch 5 that is connected to the drive source. A torque converter 6 and an automatic transmission mechanism 7 are disposed, and an output shaft of the automatic transmission mechanism 7 is connected to the wheels 8. For this reason, the driving force from the engine 2 and the motor generator 4 is alternatively or jointly transmitted through the torque converter 6 with the lockup clutch 5 and the automatic transmission mechanism 7 and transmitted to the wheels 8, so that the hybrid vehicle 1 Is driven to travel.

  Further, when the accelerator pedal 9 is released during traveling and the vehicle decelerates (coasting), the driving force from the wheels 8 is driven via the automatic transmission mechanism 7 and the torque converter 6 with the lock-up clutch 5. At this time, an engine braking action (braking action based on engine friction torque) is generated by the engine 2 and the motor generator 4 is driven to generate electric power (energy regeneration).

  The engine 2 is a multi-cylinder reciprocating type engine that can perform fuel injection control and injection fuel ignition control for each cylinder, and can perform valve operation control for closing and closing the intake and exhaust valves of each cylinder. An operation control device 3 is provided. The operation of the engine operation control device 3 is controlled by a control unit (ECU) 15 to be described later, and automatic stop / start control (so-called idle stop control) of the engine 2 is performed under predetermined operation conditions. The cylinder resting control is performed to close the intake / exhaust valves of some or all cylinders.

  The torque converter 6 can be engaged and disengaged between its input / output members (pump member and turbine member) by the lock-up clutch 5. When the lock-up clutch 5 is released, the drive source (the engine 2 and the motor generator 4). ) And the automatic transmission mechanism 7, the rotational driving force is transmitted via the torque converter 6. On the other hand, when the lockup clutch 5 is engaged, the drive source (the output shaft of the motor generator 4) and the input shaft of the automatic transmission mechanism 7 are directly connected by bypassing the torque converter 6. Engagement / disengagement control of the lockup clutch 5 is performed by a hydraulic control valve (HCV) 12, and the hydraulic control valve 12 is controlled by a control unit 15. That is, the control unit 15 performs engagement / disengagement control of the lockup clutch 5.

  The automatic transmission mechanism 7 is a stepped transmission mechanism composed of a plurality of transmission gear trains, and automatically supplies a hydraulic pressure from the hydraulic control valve 12 to the hydraulically operated transmission clutch to automatically set a desired gear stage according to the operating state. To perform automatic shifting. At this time, the hydraulic control valve 12 is controlled by the control unit 15. That is, automatic shift control according to the driving state is performed by the control unit 15.

  The motor generator 4 is driven by receiving electric power supplied from the battery 10 via the power drive unit (PDU) 11. At this time, the power drive unit 11 is controlled by the control unit 15. That is, drive control of the motor generator 4 is performed by the control unit 15. Further, when the hybrid vehicle 1 travels at a reduced speed, the motor generator 4 is rotationally driven by receiving the driving force from the wheels 8, which functions as a generator to generate a regenerative braking force, and the kinetic energy of the vehicle body is used as electric energy. The battery 10 is collected and charged via the power drive unit 11. The regenerative energy control at this time is also performed by the control unit 15 via the power drive unit 11.

  In the hybrid vehicle 1, the hydraulic pressure supply source (hydraulic pressure supply device 30) of the lock-up clutch 5 and the automatic transmission mechanism 7 includes a mechanical oil pump 20 and an electric oil pump 21. The mechanical oil pump 20 is connected to a driving source (the engine 2 and the motor generator 4), and is operated by the driving force of the driving source. In FIG. 1, the mechanical oil pump 20 is shown beside the engine 2 for the sake of simplicity, but actually, the mechanical oil pump 20 includes the torque converter 6 and the automatic transmission mechanism. 7.

  On the other hand, the electric oil pump 21 is driven by an electric motor 22. The electric motor 22 is driven by controlling the electric power supplied from the 12V battery 24 by the pump driver 23, and the pump driver 23 is controlled by the control unit 15. As described above, when the engine 2 is stopped due to the idle stop control performed by the control unit 15, the hydraulic pressure is not supplied from the mechanical oil pump 20. The motor 22 is driven and hydraulic oil is supplied from the electric oil pump 21. The electric motor 22 is a three-phase sensorless brushless motor that is more efficient than a DC brush motor, has a simpler structure, and is less expensive than a sensorless brushless motor.

  As described above, the control unit 15 controls the operation of the engine operation control device 3, the hydraulic control valve 12, the power drive unit 11, and the pump driver 23. For this control, various detection signals are input. . For example, as shown in the figure, a detection signal from the accelerator sensor 17 that detects the depression of the accelerator pedal 9 and a detection signal from the rotation speed sensor 18 that detects the input / output rotation speed of the torque converter 6 are input. The control unit 15 includes a vehicle speed detection signal from the vehicle speed sensor, an engine speed detection signal from the engine rotation sensor, a shift position detection signal of the transmission, a brake operation detection signal from the brake sensor, a remaining capacity detection signal of the battery 10, and the like. Is input.

  Now, the above-described hydraulic pressure supply device 30 will be described in more detail with reference to FIG. The hydraulic pressure supply device 30 includes an oil pan 31, a strainer 32, a first oil passage 33 connected to the strainer 32 and the suction side of the mechanical oil pump 20, a discharge side of the mechanical oil pump 20, and a first hydraulic pressure control valve 12. A third oil passage 35 branched from the second oil passage 34 and the first oil passage 33 and connected to the suction side of the electric oil pump 21, and a fourth oil passage 36 connected to the discharge side of the electric oil pump 21 and the second oil passage 34. And a fifth oil passage 37 that connects the fourth oil passage 36 and the third oil passage 35 to each other. The fourth oil passage 36 is provided with a check valve 38 so that the hydraulic oil from the mechanical oil pump 20 does not flow back to the electric oil pump 21, and the fifth oil passage 37 has a fourth oil passage. An orifice 39 and a relief valve 40 are provided in this order from the path 36 side. The relief valve 40 is configured to be opened when the oil pressure in the fourth oil passage 36 reaches a predetermined value or more, and to allow the hydraulic oil in the fourth oil passage 36 to flow into the third oil passage 35. In the following description, a circuit in which the hydraulic oil discharged from the electric oil pump 21 returns to the oil pump 21 through the fifth oil passage 37 (orifice 39, relief valve 40) is referred to as a recirculation circuit.

  When the mechanical oil pump 20 is operated by the engine 2, the hydraulic oil in the oil pan 31 is sucked into the mechanical oil pump 20 from the strainer 32 through the first oil passage 33, and is added by the mechanical oil pump 20. And is discharged to the second oil passage 34 and supplied to the hydraulic control valve 12. On the other hand, when the engine 2 is stopped and hydraulic pressure cannot be supplied by the mechanical oil pump 20, the electric oil pump 21 is operated by the control unit 15, and the operating oil of the oil pan 31 is supplied from the strainer 32 to the first oil passage 33 and the first oil passage 33. The oil is sucked into the electric oil pump 21 through the three oil passages 35, pressurized by the electric oil pump 21, discharged to the fourth oil passage 36, and supplied from the second oil passage 34 to the hydraulic control valve 12.

  Therefore, even if the engine 2 is stopped by the idle stop control, the required oil pressure is supplied by the electric oil pump 21. Therefore, the delay in the rise of the oil pressure when the engine 2 is restarted is prevented, and the start response delay is prevented. Can do. The hydraulic fluid supplied to the lockup clutch 5 and the automatic transmission mechanism 7 via the hydraulic control valve 12 is returned to the oil pan 31 via the sixth oil passage 41.

  Here, since the electric motor 22 for operating the electric oil pump 21 is a brushless sensorless motor, the electric motor 22 includes a rotor having a permanent magnet and a stator coil provided so as to surround the rotor. The rotation is controlled by adjusting the pulse voltage applied from the driver 23 to the stator coil. The pulse voltage is controlled by a pulse width modulation (PWM) method for controlling the pulse width.

  By the way, such a brushless motor needs to control the pulse voltage applied to a stator coil according to the position of the permanent magnet of a rotor. Therefore, when the electric motor 22 is started, the pump driver 23 instantaneously cuts off the power supply, causes the electric motor 22 to free run, and operates the electric motor 22 as a synchronous generator with an internal permanent magnet. It has a positioning / synchronization mode that identifies the position of the rotor from the output voltage, and the electric motor 22 can be accurately operated by controlling the pulse voltage based on the result (this state is called a sensorless mode). .

  The electric oil pump 21 used in such a hybrid vehicle 1 is necessary for maintaining the function of the automatic transmission mechanism 7 while the engine 2 is stopped in idle stop control for the purpose of saving fuel. Electric power operation is required. In order to always secure the minimum hydraulic pressure required to maintain the function of the automatic transmission mechanism 7 while the engine 2 is stopped, the electric motor 22 is controlled with a pump driving torque that is not easily affected by the oil temperature and viscosity of the hydraulic oil. It is desirable to do. Therefore, the control unit 15 outputs the magnitude of the torque that the electric motor 22 should output to the pump driver 23 as a torque command value.

  There is a proportional relationship between the output torque (pump drive torque) of the electric motor 22 and the current value of the current flowing through the stator coil (referred to as “winding current”). The current value of the winding current is measured with respect to the torque command value from the current sensor 25, and control is performed so that the measured value becomes a predetermined value, that is, a predetermined torque (this control is referred to as “torque control "). This is because if the control is performed using the voltage value applied to the electric motor 22, accurate control is more likely to be affected by changes in the applied original voltage and variations in the resistance value of the harness. .

In the hybrid vehicle 1 configured as described above, in the control unit 15, the electric motor 22 is driven and the electric oil pump 21 is operated before the vehicle speed becomes zero due to the stop of the engine 2 by the idle stop control. The relationship between the hydraulic pressure (line pressure P _L ) supplied to the hydraulic control valve 12 at this time and the hydraulic pressure (electric pump pressure P _E ) discharged from the electric oil pump 21 is as shown in FIG. That is, when the conditions for the idle stop control are met and the vehicle speed becomes slower than a predetermined value (time t ₀ in FIG. 3), the control unit 15 prepares for the idle stop control as the vehicle speed decreases, so that the control unit 15 And the electric oil pump 21 is operated. Incidentally, the electric oil pump 21 is operated requires some time to until reaching the electric oil pump pressure P _E, the time t ₁ by the electric pump pressure P _E is actually the pressure in FIG. 4 in this embodiment Is starting to rise. On the other hand, when the vehicle speed further decreases from time t ₀ to a predetermined vehicle speed (time t ₁ in FIG. 4), the engine 2 is stopped. As a result, the output of the mechanical oil pump 20 decreases and the line pressure P _L decreases. Electric pump pressure P _E is a predetermined value, i.e., (time t ₂ in FIG. 3) to reach the hydraulic P ₀ of the relief valve 40 is opened, the relief valve 40 hydraulic oil flows into Risakyu circuit open. When the line pressure P _L and the electric pump pressure P _E matches (time t ₃ in FIG. 3, the hydraulic P _1), hydraulic fluid pressure control valve discharged from the electric oil pump 21 check valve 38 is opened 12 is supplied.

  By the way, in the state where the air bubbles formed in the hydraulic circuit on the electric oil pump 21 side are included, the electric oil pump 21 sucks the air bubbles to cause an instantaneous idling. Then, only at that moment, the load acting on the electric motor 22 decreases, the torque decreases, and the winding current also decreases. Accordingly, the pump driver 23 controls the winding current to maintain the torque at the torque command value. Therefore, there is a possibility that unstable operation of the electric motor 22 is induced by a large load fluctuation.

In this embodiment, the check valve 38 is set by setting the hydraulic pressure P _{0 at} which the relief valve 40 is opened lower than the hydraulic pressure P ₁ when hydraulic oil is supplied to the hydraulic control valve 12 by the electric oil pump 21. Before the hydraulic oil is supplied from the electric oil pump 21 to the hydraulic control valve 12, the hydraulic oil can be circulated through the recirculation circuit. As a result, even if the hydraulic oil on the electric oil pump 21 side, that is, the third oil passage 35 or the fourth oil passage 36 contains air bubbles formed in the hydraulic oil, the hydraulic oil circulates through the recirculation circuit. As a result, the air bubbles are agitated and finely dispersed again, so that the electric oil pump 21 can be stably operated when the check valve 38 is opened and hydraulic oil is supplied to the hydraulic control valve 12.

  Further, a relief valve 40 is provided in the fifth oil passage 37, and is configured to be opened when the fourth oil passage 36 reaches the hydraulic pressure set in the relief valve 40 to circulate the hydraulic oil in the recirculation circuit. As a result, the minimum number of revolutions at which the electric motor 22 can operate stably can be maintained. This is because such a three-phase sensorless brushless motor has an optimum operating region, and may become unstable when operated at a low rotation outside this region.

  Further, according to the above configuration, when the hydraulic oil is supplied from the electric oil pump 21, the hydraulic oil always circulates through the recirculation circuit. Therefore, the operation discharged from the electric oil pump 21 is performed. Since the oil pulsation can be reduced, the control of the electric motor 22 in the sensorless mode can be stabilized. This is because such a sensorless brushless motor has an optimum driving load fluctuation range, and its operation may become unstable due to a sudden load fluctuation.

  Furthermore, when the required amount of hydraulic oil in the automatic transmission mechanism 7 is rapidly increased by the relief valve 40 provided in the fifth oil passage 37 and the hydraulic pressure is instantaneously reduced, the relief valve 40 is closed and flows into the recirculation circuit. Since the flow rate of the hydraulic oil can be cut, a decrease in hydraulic pressure can be prevented. Also, even when air bubbles are mixed and the oil pressure is abnormally lowered, the relief valve 40 is closed and the hydraulic oil does not circulate through the recirculation circuit, so that the air bubbles are discharged to the automatic transmission mechanism 7 and quickly become normal. Can be returned.

  As described above, the bubbles materialized in the hydraulic oil by the recirculation circuit are agitated and dispersed, but when the torque control is performed with the bubbles contained in the hydraulic oil at the start of the electric motor 22, As described above, the unstable operation of the electric motor 22 may be induced. Therefore, the pump driver 23 in the present embodiment, when receiving the torque command value from the control unit 15 and operating the electric motor 22, once rotates the electric motor 22 at a predetermined rotational speed after the positioning / synchronization mode. Control is performed to maintain this rotational speed for a predetermined time (this is referred to as “constant rotational control”), and then the control is shifted to torque control.

The processing of the pump driver 23 will be described with reference to FIGS. When the pump driver 23 receives the torque command value from the control unit 15 at time t ₁ , the pump driver 23 operates the electric motor 22 to position the rotor of the electric motor 22 in the positioning / synchronization mode, and the pulse voltage applied to the stator coil. The operation is performed at a predetermined rotational speed N ₀ (S100). When the predetermined rotational speed N ₀ is reached (time t ₂ ), constant rotational control is performed so as to maintain the rotational speed N ₀ (S101). At this time, the elapsed time from the time t ₂ at which the constant rotation control is started is measured and compared with a preset holding time t _k (S102), and when the holding time t _k elapses (time t ₂ '), the electricity The control of the motor 21 is switched to torque control, and the winding current is controlled so as to be the torque command value (S103). The time shown in FIG. 4 corresponds to the time shown in FIG. 3, in this embodiment, the electric pump pressure P _E when the constant rotational control is performed, the relief valve 40 is opened The hydraulic pressure is set to ₀ .

  When the hydraulic pressure supply device 30 according to the present embodiment is configured as described above, the relief valve 40 is opened and the hydraulic oil circulates in the recirculation circuit when the electric motor 22 is performing constant rotation control. Therefore, at the time of constant rotation control, even if the electric oil pump 21 sucks bubbles, the control of the electric motor 22 is not affected, and the bubbles are agitated and dispersed in the meantime. In addition, the load fluctuation is reduced, and the electric motor 22 and the electric oil pump 21 can be stably operated in the sensorless mode.

In addition, since a viscosity etc. change with the oil temperature, hydraulic oil changes the time when a bubble is disperse | distributed by it. That is, the lower the oil temperature of the hydraulic oil, the higher the viscosity of the hydraulic oil and the longer the time required for stirring the bubbles, and the larger the fluctuation range of the load when it cannot be dispersed, the constant rotation control holding time t _k. Need to be long.

Therefore, as shown in FIG. 6, the temperature of the hydraulic oil is measured by an oil temperature sensor 42 disposed in the oil pan 31, and the detected value is input to the control unit 15. The oil temperature of the hydraulic oil can also be passed in accordance with the torque command value being passed to 23. With this oil temperature, the pump driver 23 determines the value of the holding time t _k . The process will be described with reference to FIG. 7. After positioning the rotor of the electric motor 22 in the positioning / synchronization mode and synchronizing the pulse voltage applied to the stator coil, the motor is operated at a predetermined rotational speed N _0. (S110), advance the pump driver 23 is set to, from the map the relationship is set hold time t _k and the oil temperature, to search for the retention time t _k to oil passed from the control unit 15 temperature (S111) . Then, the constant rotation control is performed at the rotation speed N ₀ (S112), the constant rotation control is held until the elapsed time reaches the holding time tk searched from the above-mentioned map (S113), and then the control shifts to the torque control (S114). ).

Similarly, when the oil temperature of the hydraulic oil is low, the viscosity increases. Therefore, at the same rotation speed, the electric pump pressure _PE is higher than when the oil temperature is high. For this reason, when the oil temperature is low (when the viscosity is high), it is desirable to set the rotation speed low. Always maintaining a constant rotational speed in constant rotation control, when the oil temperature is low too high electric pump pressure P _E in, for interstage difference torque increases when going to the torque control, the electric motor in the sensorless mode This is because the control 22 may become unstable. Thus, by determining the rotation speed N ₀ in the constant rotation control based on the oil temperature, it is possible to maintain the minimum rotation speed at which the starting stability of the electric oil pump 21 and the electric motor 22 can be obtained.

The processing of the pump driver 23 that changes the rotation speed N ₀ of the electric motor 22 in the constant rotation control according to the oil temperature will be described with reference to FIG. When the pump driver 23 receives the torque command value and the oil temperature from the control unit 15, the pump driver 23 is passed from the control unit 15 according to a map in which the relationship between the oil temperature and the rotation speed N ₀ preset in the pump driver 23 is set. The rotation speed N ₀ corresponding to the oil temperature is searched (S120). Then, the positioning of the rotor of the electric motor 22 and the synchronization of the pulse voltage applied to the stator coil are performed in the positioning / synchronization mode, and the motor is operated at the searched rotation speed N ₀ (S121), and then the rotation speed N _0. The constant rotation control is performed so as to maintain (S122), and the constant rotation control is continued until a preset holding time t _k elapses (S123), and then the torque control is performed (S124).

Of course, the pump driver 23 searches the map for the rotation speed N ₀ in the constant rotation control and the holding time tk for holding the rotation speed N ₀ according to the oil temperature received from the control unit 15 and changes the change method. It may be realized at the same time.

In the above embodiment, the rotational speed N ₀ and the holding time t _k of the constant rotation control are set in order to disperse the bubbles in the oil passage (particularly the third oil passage 35) on the electric oil pump 21 side of the hydraulic pressure supply device 30. Although the case where the pump driver 23 is set to a preset value or is changed according to the oil temperature has been described, if there is a bubble in the third oil passage 35, the electric oil pump 21 is changed to this as shown in FIG. By sucking the bubbles, the discharged hydraulic pressure (that is, the electric pump pressure P _E ) pulsates. Therefore, as shown in FIG. 10, it provided an oil pressure sensor 43 for measuring the electric pump pressure P _E in the fourth oil passage 36, by inputting the detected value to the pump driver 23, a constant rotation control in response to the hydraulic It is also possible to configure so as to determine the timing for shifting from torque control to torque control.

The processing of the pump driver 23 to determine when to transition to the torque control from the constant rotation control by the electric pump pressure P _E will be described with reference to FIG. Upon receiving the torque command value from the controller unit 15, the pump driver 23 performs positioning of the rotor of the electric motor 22 and synchronization of the pulse voltage applied to the stator coil in the positioning / synchronization mode, and a preset rotation. After operating at the number N ₀ (S130), the rotation number N ₀ is maintained and constant rotation control is performed (S131). At this time, the fluctuation amount is obtained from the hydraulic pressure detected by the hydraulic sensor 43, and the constant rotation control is continued until the fluctuation amount becomes smaller than a predetermined value (S132). The variation amount of the hydraulic pressure becomes smaller than a predetermined value, i.e., where the pulsation of the electric pump pressure P _E has subsided, the pump driver 23 shifts the control of the electric motor 22 to the torque control based on the torque command value (S133 ).

According to this construction, since the air bubbles by the electric pump pressure P _E can be reliably detected to be distributed, the operation of the sensor-less mode of the electric oil pump 21 and the electric motor 22 after the transition to torque control It can be stabilized. Of course, as described above, the operation of the electric oil pump 21 and the electric motor 22 can be made more stable by measuring the oil temperature of the hydraulic oil and combining it with the method of changing the rotation speed N ₀ maintained by constant rotation control. Can do.

1 is a block diagram illustrating a configuration of a traveling drive system of a hybrid vehicle in which a hydraulic pressure supply device according to the present invention is used. It is a block diagram which shows the structure of the hydraulic pressure supply apparatus which concerns on this invention. It is a graph which shows transition of line pressure and electric pump pressure. It is a graph which shows transition of the rotation speed of an electric motor. It is a flowchart which shows the process in a pump driver. It is a block diagram which shows the structure of the hydraulic pressure supply apparatus in the case of controlling an electric motor with oil temperature. It is a flowchart which shows the process of the pump driver in the case of setting the holding time of constant rotation control by oil temperature. It is a flowchart which shows the process of the pump driver in the case of setting the rotation speed of constant rotation control with oil temperature. It is a graph which shows the case where an electric pump pressure pulsates. It is a block diagram which shows the structure of the hydraulic pressure supply apparatus in the case of controlling an electric motor with an electric pump pressure. It is a flowchart which shows the process of a pump driver in the case of setting the rotation speed of constant rotation control with oil temperature, and transfering to torque control with electric pump pressure.

Explanation of symbols

1 Hybrid vehicle (vehicle)
2 Engine (drive source)
4 Motor generator (drive source)
7 Automatic transmission mechanism (transmission mechanism)
8 Wheel 20 Mechanical oil pump 21 Electric oil pump 22 Electric motor 23 Pump driver 24 12V battery (battery)
30 Hydraulic supply device 37 Fifth oil passage (oil passage)
40 the relief valve 42 oil temperature sensor 43 pressure sensor t _k retention time

Claims (4)

A drive source for driving the vehicle;
  A mechanical oil pump driven by the drive source;
  An electric motor driven by a battery;
  An electric oil pump driven by the electric motor;
  Shifting with hydraulic oil supplied from the mechanical oil pump and the electric oil pump
A speed change mechanism that sets a ratio, changes the rotational driving force of the drive source, and transmits it to the wheels;
  A hydraulic pressure sensor for detecting a hydraulic pressure of the hydraulic oil discharged from the electric oil pump;
  A pump driver for controlling the operation of the electric motor,
  When the pump driver activates the electric motor, the fluctuation amount of the hydraulic pressure is a predetermined amount.
When the value is greater than or equal to the value, the electric motor is operated so that the predetermined number of rotations is obtained, and the fluctuation amount is determined.
Operates the electric motor so that a predetermined torque is output when it becomes smaller than a certain value.
A hydraulic pressure supply device configured to cause An oil temperature sensor for detecting the oil temperature of the hydraulic oil;
  The pump driver is configured to set the rotation speed according to the oil temperature.
The hydraulic pressure supply device according to claim 1. An oil passage connecting the discharge side and the suction side of the electric oil pump;
  A relief provided in the oil passage and opened when the oil pressure on the discharge side exceeds a predetermined value.
The hydraulic pressure supply device according to claim 1, further comprising a half valve. The hydraulic pressure at which the relief valve is opened is such that the electric oil pump supplies hydraulic oil to the transmission mechanism.
The hydraulic supply according to claim 3, wherein the hydraulic supply is set to a value smaller than the supplied hydraulic pressure.
Feeding device.

Images