JP2007016933A - Power output device, automobile mounted therewith, and control method for power output device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To smoothly carry out changing to an available speed-change stage during malfunction of a hydraulic circuit used for gear change. <P>SOLUTION: In the power output device, when there is a malfunction wherein both brakes B1, B2 are turned off, changing of oil circuits of control valves 112, 113 is carried out after stopping an engine 22, stopping an electric pump 104, and releasing a line pressure PL, and the electric pump 104 is controlled to gradually raise the line pressure PL to carry out changing of the brakes B1, B2. For example, when the oil passage of the control valve 113 is opened, oil passages of fail safe valves 114, 115 are both cut off, and the brakes B1, B2 are both turned off, from a state wherein the oil passage of the control valve 112 is opened, and the oil passage of the control valve 113 is cut off, and when the oil passage of the control valve 112 is cut off for carrying out changing of the brakes B1, B2, shock when the line pressure PL directly acts on the brake B2 can be suppressed by opening the fail safe valve 115. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a power output apparatus that outputs power to a drive shaft, an automobile that is mounted with the power output apparatus and that travels with an axle connected to the drive shaft, and a control method for the power output apparatus.

Conventionally, this type of power output device is mounted on a vehicle and uses a motor and two clutches that are operated by hydraulic pressure to switch the gear stage to either the Hi mode or the Lo mode to shift the power from the motor. A thing provided with the transmission which outputs is proposed (for example, refer to patent documents 1). This device is provided with a hydraulic circuit for applying hydraulic pressure to two clutches, and the hydraulic circuit is provided with a fail-safe valve that enables traveling even when an abnormality occurs in the circuit. For example, when a specific solenoid is disconnected in the Lo mode, the limp home traveling is performed by changing the traveling mode from the Lo mode to the Hi mode by switching the clutch on and off.
JP 2004-278713 A

  As described above, even when an abnormality occurs in the hydraulic circuit, it is possible to run by engaging the engageable clutch, but depending on the configuration of the hydraulic circuit and the type of abnormality, the engageable clutch When engaging, the hydraulic pressure may suddenly act on the clutch and shock may occur, or the friction material of the clutch may seize, and it is desirable to improve this.

  The power output apparatus of the present invention, the automobile equipped with the power output apparatus, and the control method of the power output apparatus can output power to the drive shaft even when an abnormality that releases any of the plurality of clutches occurs. One of the purposes. In addition, the power output apparatus of the present invention, the automobile on which the power output apparatus is mounted, and the control method of the power output apparatus can be applied regardless of whether or not an abnormality that releases any of the plurality of clutches occurs. One of the purposes is to smoothly engage the engageable clutch.

  In order to achieve at least a part of the above object, the power output apparatus of the present invention, the automobile equipped with the power output apparatus, and the control method of the power output apparatus employ the following means.

The power output apparatus of the present invention is
A power output device that outputs power to a drive shaft,
Power means capable of outputting power;
A plurality of clutches that are actuated by fluid pressure of the working fluid, with engagement of at least one of the plurality of clutches and disengagement of a clutch different from the clutch from the power means; Power transmission means capable of transmitting power to the drive shaft;
Fluid pressure generating means for generating fluid pressure;
Fluid pressure supply means capable of individually supplying the fluid pressure generated by the fluid pressure generation means to the plurality of clutch sides;
When fluid pressure is supplied only between the fluid pressure supply means and the plurality of clutches and only from the fluid pressure supply means to the engaged clutch side of the plurality of clutches, at least the fluid pressure on the clutch side When the fluid pressure is supplied from the fluid pressure supply means to the engaging clutch side of the plurality of clutches and the clutch side different from the clutch, Automatic opening / closing means for automatically interrupting the transmission of fluid pressure so that the engagement of the clutch is also released,
When an abnormality that releases the engagement of any of the plurality of clutches occurs, the fluid pressure generating means is controlled so that the fluid pressure is reduced, and after the fluid pressure is reduced, the plurality of clutches The fluid pressure supply means is arranged so that the supply of fluid pressure to the clutch side that can be engaged regardless of the abnormality is released and the supply of fluid pressure to another clutch different from the clutch is shut off. And controlling the fluid pressure generating means to control the fluid pressure generating means so that the engagement force acts on the clutch that can be engaged regardless of the abnormality by gradually increasing the fluid pressure after controlling the fluid pressure supply means. When,
It is a summary to provide.

  In this power output apparatus of the present invention, a plurality of fluid pressure supply means are interposed between a plurality of fluid pressure supply means and a plurality of clutches that can individually supply the fluid pressure generated by the fluid pressure generation means to the plurality of clutch sides. When the fluid pressure is supplied only to the clutch side of the clutch, the transmission of the fluid pressure at least on the clutch side is automatically released, and the clutch side to be engaged among the plurality of clutches from the fluid pressure supply means In the apparatus comprising an automatic opening / closing means for automatically interrupting transmission of fluid pressure so that engagement of any of the plurality of clutches is released when fluid pressure is supplied to a clutch side different from the clutch The fluid pressure generating means is controlled so that the fluid pressure is reduced when an abnormality occurs in which the engagement of any of the plurality of clutches is released; After the pressure is reduced, the supply of fluid pressure to the clutch side that can be engaged regardless of the abnormality among the plurality of clutches is released, and the supply of fluid pressure to the other clutch side different from that clutch is shut off. The fluid pressure supply means is controlled so that the fluid pressure is gradually increased after the fluid pressure supply means is controlled, and the fluid pressure generation means is controlled so that the engagement force acts on the clutch that can be engaged regardless of abnormality. . Therefore, even when an abnormality that releases any of the plurality of clutches occurs, the engageable clutch can be smoothly engaged regardless of the abnormality, and the power from the power unit is driven. Can be transmitted to the shaft. Here, the “working fluid” includes hydraulic oil.

  In such a power output apparatus of the present invention, the fluid pressure generating means includes pressure feeding means having electric pressure feeding means for pumping the working fluid using at least electric power, and the abnormality control means is any of the plurality of clutches. When an abnormality that releases the engagement of the clutch occurs, the pumping means is controlled to reduce the fluid pressure, and after the fluid pressure is reduced, the clutch is engaged regardless of the abnormality. The fluid pressure supply means is controlled so that the supply of the fluid pressure to the clutch side capable of releasing is released and the supply of the fluid pressure to another clutch different from the clutch is shut off, and the fluid pressure supply means After the control, the fluid pressure is gradually increased, and the electric pressure feeding means may be controlled so that the engagement force acts on the clutch that can be engaged regardless of the abnormality.

  In the power output device of the present invention having at least a pumping unit having an electric pumping unit, the abnormality control unit may be a unit that reduces the fluid pressure by stopping the operation of the pumping unit. it can. In this way, the fluid pressure can be reduced more appropriately.

  Further, in the power output device of the present invention having at least a pumping unit having an electric pumping unit, the power output device of the present invention further includes a temperature detection unit that detects the temperature of the working fluid pumped by the pumping unit, It may be a means for controlling the electric pumping means so that the fluid pressure is increased with a sweep gradient based on the detected temperature of the working fluid. In this case, the sweep gradient may be a gradient set so as to increase as the detected temperature of the working fluid decreases. In this way, it is possible to smoothly engage the clutch that can be engaged regardless of the abnormality regardless of the temperature of the working fluid.

  Furthermore, in the power output apparatus of the present invention having at least a pressure feeding means having an electric pressure feeding means, the abnormal time control means prepares for applying an engagement force to a clutch that can be engaged regardless of the abnormality. The electric pressure feeding means is controlled to be executed over a period of time, and the electric pressure feeding means is controlled so that an increase in engagement force of a clutch that can be engaged regardless of the abnormality is started after the preparation is completed. It can also be a means. In this way, the clutch that can be engaged regardless of the abnormality can be engaged more quickly. Here, “preparation” includes a fast fill that temporarily increases the amount of working fluid pumped from the electric pumping means. The power output device of this aspect of the present invention includes temperature detection means for detecting the temperature of the working fluid pumped by the pumping means, and the predetermined time is set based on the detected temperature of the working fluid. It can also be time. In this case, the predetermined time may be a time that is set to become longer as the detected temperature of the working fluid is lower. In this way, preparation for applying the engagement force to the clutch can be executed more appropriately regardless of the temperature of the working fluid.

  In the power output apparatus of the present invention, the abnormality control means may be a means that functions while the drive shaft is rotating. By doing so, the effect of smoothly engaging the clutch that can be engaged regardless of abnormality becomes more remarkable.

  In the power output apparatus of the present invention, the power means may be an electric motor.

  In the power output apparatus of the present invention, the power transmission means may be a transmission mechanism that transmits power with a changeable gear ratio.

The automobile of the present invention
The power output device of the present invention according to any one of the above-described aspects, in particular, basically a power output device that outputs power to the drive shaft, and a power means capable of outputting power, and a fluid pressure of the working fluid A plurality of clutches operated by the at least one clutch of the plurality of clutches and the disengagement of a clutch different from the clutches, and the power from the power means to the drive shaft Transmittable power transmitting means, fluid pressure generating means for generating fluid pressure, fluid pressure supplying means capable of individually supplying fluid pressure generated by the fluid pressure generating means to the plurality of clutch sides, and the fluid When fluid pressure is supplied only between the pressure supply means and the plurality of clutches from the fluid pressure supply means to the engaged clutch side of the plurality of clutches, at least on the clutch side. When the fluid pressure is automatically released and the fluid pressure is supplied from the fluid pressure supply means to the clutch side to be engaged among the plurality of clutches and the clutch side different from the clutch, Automatic opening / closing means for automatically interrupting transmission of fluid pressure so that any clutch is disengaged, and fluid pressure when an abnormality occurs in which any of the plurality of clutches is disengaged After the fluid pressure generating means is controlled to reduce the fluid pressure and the fluid pressure is reduced, the supply of fluid pressure to the clutch side that can be engaged regardless of the abnormality among the plurality of clutches is released. The fluid pressure supply means is controlled so that the supply of fluid pressure to another clutch different from the clutch is cut off, and the fluid pressure is gradually increased after the fluid pressure supply means is controlled. Regardless of this, it is equipped with a power output device including an abnormality control means for controlling the fluid pressure generating means so that an engaging force is applied to a clutch that can be engaged, and travels with an axle connected to the drive shaft. Is the gist.

  In this automobile of the present invention, since the power output device of the present invention according to any one of the above-described aspects is mounted, the same effect as the effect of the power output device of the present invention, for example, any of a plurality of clutches Even when an abnormality that releases the engagement occurs, the effect that the clutch that can be engaged can be smoothly engaged and power can be output to the drive shaft regardless of the abnormality can be exhibited. Here, the “abnormality control means” can also function during traveling.

The method for controlling the power output apparatus of the present invention includes:
Power means capable of outputting power, and a plurality of clutches operated by fluid pressure of the working fluid, and engagement of at least one of the plurality of clutches and disengagement of a clutch different from the clutch Power transmission means capable of transmitting power from the power means to the drive shaft, fluid pressure generation means for generating fluid pressure, and fluid pressure generated by the fluid pressure generation means to the plurality of clutch sides. Fluid pressure supply means that can be supplied individually, and fluid pressure is supplied only between the fluid pressure supply means and the clutch side to be engaged among the plurality of clutches, interposed between the fluid pressure supply means and the plurality of clutches. When this is done, at least the transmission of fluid pressure on the clutch side is automatically released, and the clutch side engaged with the clutches from the fluid pressure supply means is different from the clutch. An automatic opening / closing means for automatically interrupting transmission of fluid pressure so that engagement of any of the plurality of clutches is released when fluid pressure is supplied to the clutch side. A control method,
(A) controlling the fluid pressure generating means so that the fluid pressure is reduced when an abnormality that releases the engagement of any of the plurality of clutches occurs;
(B) After the fluid pressure is reduced, supply of fluid pressure to the clutch side that can be engaged regardless of the abnormality among the plurality of clutches is released, and to other clutches different from the clutch Controlling the fluid pressure supply means so that the supply of fluid pressure is interrupted;
(C) The fluid pressure generating means is controlled so that the engagement force acts on the clutch that can be engaged regardless of the abnormality by gradually increasing the fluid pressure after controlling the fluid pressure supplying means. To do.

  According to the control method of the power output device of the present invention, the fluid pressure generated by the fluid pressure generating means is interposed between the plurality of clutches and the fluid pressure supplying means capable of individually supplying the fluid pressure to the plurality of clutch sides. When the fluid pressure is supplied from the pressure supply means only to the clutch side to be engaged among the plurality of clutches, at least the transmission of the fluid pressure on the clutch side is automatically released and the fluid pressure supply means is engaged in the plurality of clutches. When the hydraulic pressure is supplied to the clutch side that is different from the clutch side and the clutch side that is different from the clutch, the automatic release cutoff that automatically shuts off the transmission of the fluid pressure so that the engagement of any of the plurality of clutches is released And a fluid pressure generating means for reducing the fluid pressure when an abnormality occurs in which the engagement of any of the plurality of clutches is released. After controlling and reducing the fluid pressure, the supply of fluid pressure to the clutch side that can be engaged regardless of abnormality among the plurality of clutches is released and the fluid pressure to the other clutch side different from that clutch The fluid pressure supply means is controlled so that the supply of the fluid is cut off, and after the fluid pressure supply means is controlled, the fluid pressure is gradually increased so that the engagement force acts on the clutch that can be engaged regardless of abnormality. Control the generating means. Therefore, even when an abnormality that releases any of the plurality of clutches occurs, the engageable clutch can be smoothly engaged regardless of the abnormality, and the power from the power unit is driven. Can be transmitted to the shaft. Here, the “working fluid” includes hydraulic oil.

  Next, the best mode for carrying out the present invention will be described using examples.

  FIG. 1 is a configuration diagram showing an outline of the configuration of a hybrid vehicle 20 equipped with a power output apparatus as an embodiment of the present invention. As shown in the figure, the hybrid vehicle 20 of the embodiment includes an engine 22, a three-shaft power distribution / integration mechanism 30 connected to a crankshaft 26 as an output shaft of the engine 22 via a damper 28, and power distribution / integration. A motor MG1 capable of generating electricity connected to the mechanism 30, a motor MG2 connected to the power distribution and integration mechanism 30 via a transmission 60, and a hybrid electronic control unit 70 for controlling the entire drive system of the vehicle.

  The engine 22 is an internal combustion engine that outputs power using a hydrocarbon-based fuel such as gasoline or light oil, and an engine electronic control unit (hereinafter referred to as an engine ECU) that receives signals from various sensors that detect the operating state of the engine 22. ) 24 is subjected to operation control such as fuel injection control, ignition control, intake air amount adjustment control and the like. The engine ECU 24 is in communication with the hybrid electronic control unit 70, controls the operation of the engine 22 by a control signal from the hybrid electronic control unit 70, and, if necessary, transmits data related to the operating state of the engine 22 to the hybrid electronic control. Output to unit 70.

  The power distribution and integration mechanism 30 includes an external gear sun gear 31, an internal gear ring gear 32 arranged concentrically with the sun gear 31, a plurality of pinion gears 33 that mesh with the sun gear 31 and mesh with the ring gear 32, A planetary gear mechanism is provided that includes a carrier 34 that holds a plurality of pinion gears 33 so as to rotate and revolve, and that performs differential action using the sun gear 31, the ring gear 32, and the carrier 34 as rotational elements. In the power distribution and integration mechanism 30, the crankshaft 26 of the engine 22 is connected to the carrier 34, the motor MG1 is connected to the sun gear 31, and the motor MG2 is connected to the ring gear 32 via the transmission 60. The motor MG1 generates power. When the motor MG1 functions as a motor, the power from the engine 22 input from the carrier 34 is distributed according to the gear ratio between the sun gear 31 side and the ring gear 32 side, and when the motor MG1 functions as an electric motor, the engine 22 input from the carrier 34. And the power from the motor MG1 input from the sun gear 31 are integrated and output to the ring gear 32. The ring gear 32 is mechanically connected to the drive wheels 39a and 39b via a gear mechanism 37 and a differential gear 38. Therefore, the power output to the ring gear 32 is output to the drive wheels 39a and 39b via the gear mechanism 37 and the differential gear 38.

  Both the motor MG1 and the motor MG2 are configured as well-known synchronous generator motors that can be driven as generators and can be driven as motors, and exchange power with the battery 50 via inverters 41 and 42. The power line 54 connecting the inverters 41 and 42 and the battery 50 is configured as a positive and negative bus shared by the inverters 41 and 42, and the electric power generated by one of the motors MG 1 and MG 2 is supplied to another motor. It can be consumed at. Therefore, battery 50 is charged / discharged by electric power generated from motors MG1 and MG2 or insufficient electric power. Note that the battery 50 is not charged / discharged if the electric power balance is balanced by the motor MG1 and the motor MG2. The motors MG1 and MG2 are both driven and controlled by a motor electronic control unit (hereinafter referred to as a motor ECU) 40. The motor ECU 40 detects signals necessary for driving and controlling the motors MG1 and MG2, such as signals from rotational position detection sensors 43 and 44 that detect the rotational positions of the rotors of the motors MG1 and MG2, and current sensors (not shown). The phase current applied to the motors MG1 and MG2 to be applied is input, and a switching control signal to the inverters 41 and 42 is output from the motor ECU 40. The motor ECU 40 calculates the rotational speeds Nm1 and Nm2 of the rotors of the motors MG1 and MG2 by a rotational speed calculation routine (not shown) based on signals input from the rotational position detection sensors 43 and 44. The motor ECU 40 is in communication with the hybrid electronic control unit 70, controls the driving of the motors MG1 and MG2 by a control signal from the hybrid electronic control unit 70, and, if necessary, data on the operating state of the motors MG1 and MG2. Output to the hybrid electronic control unit 70.

  The transmission 60 connects and disconnects the rotating shaft 48 of the motor MG2 and the ring gear shaft 32a and reduces the rotational speed of the rotating shaft 48 of the motor MG2 to two stages by connecting the both shafts to the ring gear shaft 32a. It is configured to be able to communicate. An example of the configuration of the transmission 60 is shown in FIG. The transmission 60 shown in FIG. 2 includes a double-pinion planetary gear mechanism 60a, a single-pinion planetary gear mechanism 60b, and two brakes B1 and B2. The planetary gear mechanism 60a of a double pinion includes an external gear sun gear 61, an internal gear ring gear 62 arranged concentrically with the sun gear 61, a plurality of first pinion gears 63a meshing with the sun gear 61, and the first pinion gear 63a. A plurality of second pinion gears 63b that mesh with the one pinion gear 63a and mesh with the ring gear 62, and a carrier 64 that holds the plurality of first pinion gears 63a and the plurality of second pinion gears 63b so as to rotate and revolve freely. The sun gear 61 can be freely rotated or stopped by turning on and off the brake B1. The single-pinion planetary gear mechanism 60 b includes an external gear sun gear 65, an internal gear ring gear 66 disposed concentrically with the sun gear 65, and a plurality of pinion gears 67 that mesh with the sun gear 65 and mesh with the ring gear 66. And a carrier 68 that holds a plurality of pinion gears 67 so as to rotate and revolve. The sun gear 65 is connected to the rotating shaft 48 of the motor MG2, the carrier 68 is connected to the ring gear shaft 32a, and the ring gear 66 is braked. The rotation can be freely or stopped by turning on and off B2. The double pinion planetary gear mechanism 60a and the single pinion planetary gear mechanism 60b are connected by a ring gear 62 and a ring gear 66, and a carrier 64 and a carrier 68, respectively. The transmission 60 can disconnect the rotating shaft 48 of the motor MG2 from the ring gear shaft 32a by turning off both the brakes B1 and B2, and can turn off the brake B1 and turn on the brake B2 to turn on the rotating shaft 48 of the motor MG2. Is rotated at a relatively large reduction ratio and transmitted to the ring gear shaft 32a (hereinafter, this state is referred to as a Lo gear state), the brake B1 is turned on and the brake B2 is turned off to rotate the rotating shaft 48 of the motor MG2. Is rotated at a relatively small reduction ratio and transmitted to the ring gear shaft 32a (hereinafter, this state is referred to as a Hi gear state). Note that when the brakes B1 and B2 are both turned on, the rotation of the rotary shaft 48 and the ring gear shaft 32a is prohibited.

  The brakes B1 and B2 are turned on and off by the hydraulic pressure from the hydraulic circuit 100 illustrated in FIG. As shown in the figure, the hydraulic circuit 100 includes a mechanical pump 102 that pumps oil by the power from the engine 22, an electric pump 104 that pumps oil by the power from the built-in motor 103, a mechanical pump 102, A three-way solenoid 105 and a pressure control valve 106 that can switch the pressure (line pressure) of oil pumped from the pump 104, and a linear that can be individually supplied to the brakes B1 and B2 with adjustable pressure. Solenoids 110, 111 and control valves 112, 113, modulator valve 108 that reduces the line pressure and supplies it to the input ports of 3-way solenoid 105 and linear solenoids 110, 111, control valves 112, 113, and brakes B1, B2 Oil passage between When hydraulic pressure is supplied from either one of the control valves 112 and 113, the oil passage to the corresponding brake is opened and the oil passage to the other brake is shut off, and the hydraulic pressure is supplied from both the control valves 112 and 113. Fail-safe valves 114 and 115 that shut off both of the oil passages to the brakes B1 and B2 when an abnormality is supplied, and an accumulator 116 provided in the oil passage between the fail-safe valves 114 and 115 and the brakes B1 and B2. 117.

  FIG. 4 is an explanatory diagram showing an example of the operation of the failsafe valves 114 and 115. 4A shows a normal operation in which the hydraulic pressure is supplied from the control valve 112 and the hydraulic pressure from the control valve 113 is cut off, and FIG. 4B shows the hydraulic pressure from both the control valves 112 and 113. Shows the operation at the time of an abnormal supply. As shown in the figure, the fail-safe valves 114 and 115 are configured such that the spools 114b and 115b are urged downward in the figure by springs 114a and 115a, and the modulator valves 108 are moved in a direction to move the spools 114b and 115b upward in the figure. The hydraulic pressure from the control valve 113 is introduced in the direction in which the spool 114b is moved downward in the figure, and the hydraulic pressure from the control valve 112 is introduced in the direction in which the spool 115b is moved downward in the figure. It has become. Therefore, when the hydraulic pressure is supplied from the control valve 112 and the supply of the hydraulic pressure from the control valve 113 is interrupted, as shown in FIG. 4A, in the fail-safe valve 114, the hydraulic pressure from the modulator valve 108 is changed to the spring 114a. The spool 114b is moved upward in the figure by overcoming the urging force of the valve to open the oil passage between the control valve 112 and the brake B1, and the fail-safe valve 115 has the hydraulic pressure from the control valve 112 and the urging force of the spring 115a. Thus, the oil pressure from the modulator valve 108 is overcome, and the spool 115b is moved downward in the figure to block the oil path between the control valve 113 and the brake B2. Similarly, when the supply of hydraulic pressure from the control valve 112 is shut off and the hydraulic pressure from the control valve 113 is supplied, the fail-safe valve 114 shuts off the oil path between the control valve 112 and the brake B1 and fails. In the safe valve 115, the oil path between the control valve 113 and the brake B2 is opened. On the other hand, when an abnormality occurs in which the hydraulic pressure is supplied from both the control valves 112 and 113, as shown in FIG. 4B, the fail safe valve 114 moves the spool 114b downward by the hydraulic pressure from the control valve 113 as shown in FIG. In this manner, the oil path between the control valve 112 and the brake B1 is shut off, and the fail safe valve 115 moves the spool 115b downward in the drawing by the hydraulic pressure from the control valve 112 to shut off the oil path between the control valve 113 and the brake B2. To do. As a result, the brakes B1 and B2 are both turned off, and the rotation shaft 48 and the ring gear shaft 32a of the motor MG2 are disconnected. As described above, when the brakes B1 and B2 are both on, the rotation of the rotating shaft 48 and the ring gear shaft 32a of the motor MG2 is prohibited. If this occurs while the vehicle is running, a large shock may occur in the vehicle. Since the brakes B1 and B2 are seized, the brakes B1 and B2 are both prevented from being turned on by the fail-safe valves 114 and 115 even when hydraulic pressure is supplied from both the control valves 112 and 113 due to some abnormality. It is doing. When an abnormality occurs in which the supply of hydraulic pressure from both the control valves 112 and 113 is interrupted, the line pressure PL is shut off by the control valves 112 and 113. In this case, both the brakes B1 and B2 are turned off. Will be.

  The battery 50 is managed by a battery electronic control unit (hereinafter referred to as a battery ECU) 52. The battery ECU 52 receives signals necessary for managing the battery 50, for example, a voltage between terminals from a voltage sensor (not shown) installed between the terminals of the battery 50, and a power line 54 connected to the output terminal of the battery 50. The charging / discharging current from the attached current sensor (not shown), the battery temperature from the temperature sensor (not shown) attached to the battery 50, and the like are input. Output to the control unit 70. The battery ECU 52 also calculates the remaining capacity (SOC) based on the integrated value of the charge / discharge current detected by the current sensor in order to manage the battery 50.

  The hybrid electronic control unit 70 is configured as a microprocessor centered on the CPU 72, and in addition to the CPU 72, a ROM 74 for storing processing programs, a RAM 76 for temporarily storing data, an input / output port and communication not shown. And a port. The hybrid electronic control unit 70 includes an ignition signal from an ignition switch 80, a shift position SP from a shift position sensor 82 that detects the operation position of the shift lever 81, and an accelerator pedal position sensor 84 that detects the amount of depression of the accelerator pedal 83. From the hydraulic switch 120 that is turned on and off by the line pressure in the hydraulic circuit 100, the brake pedal position BP from the brake pedal position sensor 86 that detects the depression amount of the brake pedal 85, the vehicle speed V from the vehicle speed sensor 88, and the line pressure in the hydraulic circuit 100 The hydraulic pressure switch that is turned on / off by the line pressure PL, the oil temperature To from the temperature sensor 121 that detects the temperature of the oil pumped by the mechanical pump 102 or the electric pump 104, and the hydraulic pressure acting on the brake B1. Brake pressure Pb1 from 122, a brake pressure Pb2 from a hydraulic switch 123 that turns on and off by hydraulic pressure acting on the brake B2 is input via the input port. The hybrid electronic control unit 70 outputs drive signals to the three-way solenoid 105 and the linear solenoids 110 and 111. As described above, the hybrid electronic control unit 70 is connected to the engine ECU 24, the motor ECU 40, and the battery ECU 52 via communication ports, and exchanges various control signals and data with the engine ECU 24, the motor ECU 40, and the battery ECU 52. Is doing.

  The hybrid vehicle 20 of the embodiment thus configured calculates the required torque to be output to the ring gear shaft 32a as the drive shaft based on the accelerator opening Acc and the vehicle speed V corresponding to the depression amount of the accelerator pedal 83 by the driver. Then, the operation of the engine 22, the motor MG1, and the motor MG2 is controlled so that the required power corresponding to the required torque is output to the ring gear shaft 32a. As operation control of the engine 22, the motor MG1, and the motor MG2, the operation of the engine 22 is controlled so that power corresponding to the required power is output from the engine 22, and all of the power output from the engine 22 is the power distribution and integration mechanism 30. Torque conversion operation mode for driving and controlling the motor MG1 and the motor MG2 so that the torque is converted by the motor MG1 and the motor MG2 and output to the ring gear shaft 32a, and the required power and the power required for charging and discharging the battery 50. The engine 22 is operated and controlled so that suitable power is output from the engine 22, and all or part of the power output from the engine 22 with charging / discharging of the battery 50 is the power distribution and integration mechanism 30, the motor MG1, and the motor. The required power is converted to the ring gear shaft 32 with torque conversion by MG2. Charge / discharge operation mode in which the motor MG1 and the motor MG2 are driven and controlled to be output to each other, and a motor operation mode in which the operation of the engine 22 is stopped and the power corresponding to the required power from the motor MG2 is output to the ring gear shaft 32a. and so on.

  Next, the operation of the hybrid vehicle 20 according to the embodiment, particularly, the operation when an abnormality occurs in which both the brakes B1 and B2 of the transmission 60 are turned off while traveling will be described. FIG. 5 is a flowchart illustrating an example of a brake abnormality control routine executed by the hybrid electronic control unit 70 of the hybrid vehicle 20 according to the embodiment. Here, the determination as to whether or not an abnormality has occurred in which both the brakes B1 and B2 are turned off during traveling is, for example, whether or not the vehicle speed V from the vehicle speed sensor 88 is equal to or higher than a predetermined vehicle speed (for example, 20 km / h). Alternatively, the transmission 60 is obtained by reducing the rotational speed Nm2 of the motor MG2 calculated based on the rotational position of the rotor of the motor MG2 from the rotational position detection sensor 44 by the rotational speed Nr of the ring gear shaft 32a (Nm2 / Nr). This is performed by determining whether or not the gear ratio exceeds the range of the gear ratio that can normally be taken. The rotation speed Nr of the ring gear shaft 32a can be obtained by multiplying the vehicle speed V by the conversion factor k.

  When the brake abnormality control routine is executed, the CPU 72 of the hybrid electronic control unit 70 firstly changes the line pressure PL from the hydraulic switch 120, the brake pressures Pb1 and Pb2 from the hydraulic switches 122 and 123, and the shift of the transmission 60. Data such as a status flag F is input (step S100). Here, the shift state flag F is set to a value of 1 when switching from the Lo gear to the Hi gear in the transmission 60 is started, and set to a value of 0 when the switching from the Hi gear to the Lo gear is started. The data written in a predetermined area of the RAM 76 is input by reading. Therefore, when the switching from the Lo gear to the Hi gear is started, the shift state flag F has a value of 1 until the switching from the Hi gear to the next time the switching from the Hi gear to the Lo gear is started. Is set, and when switching from the Hi gear to the Lo gear is started, the value 0 is set until the switching from the Lo gear to the Hi gear is started after the switching from the Lo gear is completed. It will be.

  When the data is thus input, it is determined whether or not the line pressure PL is ON and the brake pressures Pb1 and Pb2 of the brakes B1 and B2 are both OFF (steps S110 and S120). This determination is that the abnormality in which both the brakes B1 and B2 are turned off is caused by the release of the line pressure PL or the release of the brake pressures Pb1 and Pb2 although the line pressure PL is not released. This is for determining whether or not the brakes B1 and B2 can be switched. If the line pressure PL is determined to be OFF, the brake pressure Pb1 is determined to be ON, or the brake pressure Pb2 is determined to be ON, it is determined that the switching between the brakes B1 and B2 cannot be performed, and this routine is terminated. To do. In this case, the power from the motor MG2 is not transmitted to the ring gear shaft 32a, but travels by stopping the motor MG2 and outputting the power from the engine 22 directly to the ring gear shaft 32a while receiving the torque reaction force at the motor MG1. I can.

  On the other hand, when it is determined that the line pressure PL is ON and the brake pressures Pb1 and Pb2 of the brakes B1 and B2 are both OFF, the operation of the engine 22 is stopped (step S130), and the operation of the electric pump 104 is stopped (step S130). In step S140, the process waits until the line pressure PL from the hydraulic switch 120 is OFF, that is, the line pressure PL is released (steps S150 and S160). In the embodiment, it is determined whether or not the line pressure has been released based on the line pressure PL from the hydraulic switch 120. However, the time required for the line pressure PL to be released is obtained in advance through experiments and the like. It is also possible to wait until elapses.

  When the line pressure PL is released, the shift state flag F input in step S100 is checked (step S170). When the shift state flag F is determined to be 1, the transmission 60 is in the Hi gear state or from the Lo gear to the Hi gear. In order to switch from the brake B1 to the brake B2, it is determined that an abnormality has occurred during the switching, that is, the brake B1 is turned on or the brake B1 is about to be turned on. The linear solenoids 110 and 111 are controlled so that the linear solenoid 110 on the brake B1 side is driven with a duty ratio of 0% and the linear solenoid 111 on the side of the brake B2 is driven with a duty ratio of 100% (step S180). When the state flag F is determined to be 0, whether the transmission 60 is in the Lo gear state or the Hi gear From the brake B2 to the brake B1, it is determined that an abnormality has occurred while switching to the Lo gear, that is, the brake B2 is turned on or the brake B2 is about to be turned on. Therefore, the linear solenoids 110 and 111 are controlled so that the linear solenoid 110 on the brake B1 side is driven with a duty ratio of 100% and the linear solenoid 111 on the side of the brake B2 is driven with a duty ratio of 0% (step). S190). The case where the oil passage of the control valve 112 is opened due to some abnormality from the state where the oil passage of the control valve 112 is opened and the oil passage of the control valve 113 is shut off and the brake B1 is turned on and the brake B2 is turned off. Think. In this case, as described above, since the oil passages between the control valves 112 and 113 and the brakes B1 and B2 are both shut off by the operation of the failsafe valves 114 and 115, the line pressure PL is reduced to the failsafe valves 114 and 115. At 115, the brake is cut off, and both the brakes B1 and B2 are turned off. In this state, if the oil passage of the control valve 112 is shut off and the switching from the brake B1 to the brake B2 is performed directly while maintaining the line pressure PL, the fail-safe valve is accompanied with the shutoff of the oil passage of the control valve 112. 115 is opened, and the oil passage of the control valve 113 is opened due to an abnormality, so that the line pressure PL acts directly on the brake B2 via the control valve 113 and the fail-safe valve 115, and a large shock is generated or braked. The friction material of B2 may be seized. When an abnormality occurs in which both the brakes B1 and B2 are turned off, the line pressure PL is temporarily released because one of the oil passages of the control valves 112 and 113 is opened and the other is shut off due to some abnormality. This is to prevent the occurrence of a large shock due to the direct action of the line pressure PL on the brake when the brakes B1 and B2 are switched while the oil passages of the valves 112 and 113 are both open.

  When the linear solenoids 110 and 111 are controlled in this manner, the drive control of the electric pump 104 is started by starting the execution of the electric pump drive control routine illustrated in FIG. 6 (step S200), and the switching of the brakes B1 and B2 is completed. (Step S210), and this routine is finished. Here, whether or not the switching of the brakes B1 and B2 has been completed is determined based on the gear ratio of the transmission 60 after the switching of the brakes B1 and B2 and the rotational speed Nr of the ring gear shaft 32a after the switching of the motor MG2. By estimating the number Nm2 * and comparing the estimated rotation number Nm2 * after switching with the rotation number Nm2 of the motor MG2 calculated based on the rotation position of the rotor of the motor MG2 from the rotation position detection sensor 44. Can be done. As a result, the rotation shaft 48 of the motor MG1 and the ring gear shaft 32a are connected again by switching between the brakes B1 and B2, and the power from the motor MG2 can be output to the ring gear shaft 32a to travel. If a predetermined time elapses without completing the switching of the brakes B1 and B2 (step S220), it is determined that another abnormality incapable of switching the brakes B1 and B2 has occurred, and the switching of the brakes B1 and B2 is performed. This routine is terminated without completing the above. Here, in the embodiment, a predetermined time is used as a time longer than the time normally required for switching between the brakes B1 and B2.

  Next, the electric pump drive control routine illustrated in FIG. 6 in step S200 will be described. When the electric pump drive control routine is executed, the CPU 72 of the hybrid electronic control unit 70 first inputs the oil temperature To from the oil temperature sensor 121 (step S300), and fast fill based on the input oil temperature To. Time Tf is set (step S310). Here, the fast fill is a process of rapidly filling the pack with oil in order to fill the gap until the friction material is applied to the brake. The setting of the fast fill time Tf as the execution time is as follows: The relationship between the oil temperature To and the fast fill time Tf is obtained in advance and stored as a map, and when the oil temperature To is given, the corresponding fast fill time Tf is derived from the stored map. . An example of this map is shown in FIG. As shown in the figure, the fast fill time Tf is set so as to become longer because the oil viscosity becomes larger and the oil is less likely to be pumped from the electric pump 104 as the oil temperature To becomes lower. When the fast fill time Tf is set, the fast fill rotation speed N1 is set to the target rotation speed Nopm of the electric pump 104 and is electrically driven to rotate at the set target rotation speed Nopm until the set fast fill time Tf elapses. Drive control of the pump 104 is performed (steps S320 to S340). Here, in the embodiment, the fast fill rotation speed N1 is set to a predetermined value so that the electric pump 104 is driven to rotate at a rotation speed near or slightly lower than the upper limit rotation speed.

  When the fast fill time Tf has elapsed, next, the low pressure standby rotation speed N2 lower than the fast fill rotation speed N1 is set as the target rotation speed Nopm of the electric pump 104 and the set target until the inertia phase starts. The electric pump 104 is driven and controlled to rotate at the rotation speed Nopm (steps S350 to S370). Here, whether or not the inertia phase has started can be determined based on a change in the rotational speed of the motor MG2 (for example, a difference between the current rotational speed Nm2 of the motor MG2 and the previous rotational speed). When the inertia phase is started, the sweep gradient ΔN is set based on the oil temperature To input in step S300 (step S380). In this embodiment, the sweep gradient ΔN is set from the map stored in the ROM 74 by previously obtaining the relationship between the oil temperature To and the sweep gradient ΔN and storing it in the ROM 74 as a map. This was performed by deriving a sweep gradient ΔN. An example of this map is shown in FIG. As shown in the figure, the sweep gradient ΔN is set such that the lower the oil temperature To, the greater the viscosity of the oil, and the more difficult the oil is pumped from the electric pump 104, so the gradient becomes steeper (the value increases). It was supposed to be. When the sweep gradient ΔN is set, a value obtained by adding the set sweep gradient ΔN to the previous value (previous Nopm) of the target rotation speed Nopm is set as a new target rotation speed Nopm and is rotated at the set target rotation speed Nopm. The process for driving and controlling the electric pump 104 (steps S390 and S400) is repeatedly executed until the switching of the brakes B1 and B2 is completed (step S410), and this routine is finished when the switching of the brakes B1 and B2 is completed. .

  FIG. 9 shows the line pressure PL, the duty ratios of the linear solenoids 110 and 111, and the target rotational speed Nopm of the electric pump 104 when the brake B1 is on and the brake B2 is off. Explanatory drawing which shows the mode of a time change is shown. When the brakes B1 and B2 are both turned off, the operation of the engine 22 is stopped, the operation of the electric pump 104 is stopped, the line pressure PL is once released, and then the linear solenoid 110 is driven at a duty ratio of 0%. At the same time, by driving the linear solenoid 111 with a duty ratio of 100%, the oil passage of the control valve 112 corresponding to the brake B1 is shut off and the oil passage of the control valve 113 corresponding to the brake B2 is opened. At this time, since the line pressure PL is released, even if the oil passages of the control valves 112 and 113 are both opened due to some abnormality, the oil passage of the fail-safe valve 114 is opened due to the oil passage of the control valve 112 being blocked. Therefore, even if the line pressure PL acts directly on the brake B2, a large shock does not occur. Then, the electric pump 104 performs the fast fill with the fast fill time Tf based on the oil temperature To, and pumps the oil from the electric pump 104 with the sweep gradient ΔN based on the oil temperature To, thereby gradually increasing the engagement force. Switching from B1 to brake B2 is performed. Thereby, even when an abnormality occurs in which the oil passages of the control valves 112 and 113 are both opened, it is possible to smoothly shift to a usable gear stage. Even when the brakes B1 and B2 are both turned off due to an abnormality from the state in which the brake B1 is off and the brake B2 is on, switching from the brake B2 to the brake B1 can be performed by the same operation.

  According to the hybrid vehicle 20 of the embodiment described above, when hydraulic pressure is supplied from either one of the control valves 112 and 113 provided in the oil passage between the control valves 112 and 113 and the brakes B1 and B2, respectively. Fail to open the oil path to the corresponding brake, shut off the oil path to the other brake, and shut off both of the oil paths to the brakes B1 and B2 in the event of an abnormal supply of hydraulic pressure from both control valves 112 and 113 In the case where the hydraulic circuit 100 provided with the safe valves 114 and 115 is provided, when an abnormality occurs in which the brakes B1 and B2 are both turned off during traveling, the operation of the mechanical pump 102 and the operation of the electric pump 104 are performed. Once the line pressure PL is released and the line pressure PL is released The linear solenoids 110 and 111 are controlled so that the oil passages of the roll valves 112 and 113 are switched, and thereafter, the electric pump 104 is driven and controlled so that the line pressure PL gradually increases to switch the brakes B1 and B2. Thus, even when an abnormality occurs in which the hydraulic pressure is supplied from both the control valves 112 and 113 due to some abnormality, the switching of the brakes B1 and B2 can be performed smoothly. Moreover, since the electric pump 104 is driven and controlled by setting the fast fill time Tf or setting the sweep gradient ΔN based on the temperature of the oil pumped by the electric pump 104 (oil temperature To), the oil temperature To Regardless, the brakes B1 and B2 can be appropriately switched.

  In this embodiment, the motor MG2 corresponds to power means, the transmission 60 corresponds to power transmission means, and the mechanical pump 102, the electric pump 104, the 3-way solenoid 105, and the pressure control valve 106 are fluid pressure generating means. The fail safe valves 114 and 115 correspond to the automatic opening / closing means, and the hybrid electronic control unit 70 that executes the brake abnormality control routine illustrated in FIG. 5 and the electric pump drive control routine illustrated in FIG. It corresponds to the control means at the time of abnormality.

  In the hybrid vehicle 20 of the embodiment, the fast fill time Tf is set based on the oil temperature To and the sweep gradient ΔN is set. However, the fast fill time Tf is set based on the oil temperature To and the sweep gradient ΔN is set. May be used as the predetermined value, the fast fill time Tf may be used as the predetermined value, and the sweep gradient ΔN may be set based on the oil temperature To, or the fast fill time Tf may be used as the predetermined value and the sweep may be performed. The gradient ΔN may be used as a predetermined value.

  In the hybrid vehicle 20 of the embodiment, when an abnormality is detected in which both the brakes B1 and B2 are turned off, the line pressure PL is once released, the oil passages of the control valves 112 and 113 are switched, and the line pressure is again applied. The brakes B1 and B2 are switched by increasing PL. However, when both brakes B1 and B2 are turned off, one of the oil passages of the control valves 112 and 113 is opened and the other is shut off. In addition to the abnormality in which the oil passages of the control valves 112 and 113 are both opened from the state in which the control valves 112 and 113 are open, one of the oil passages of the control valves 112 and 113 is open and the other is shut off. Includes an abnormality that shuts off both the oil and the oil passages of the control valves 112 and 113 are both shut off Further, when both the brakes B1 and B2 are turned off, even if the line pressure PL is maintained, the oil of the control valve whose oil path is shut off before the abnormality occurs in the control valves 112 and 113. If the road is gradually opened, the line pressure PL does not directly act on the brake. Therefore, the brakes B1 and B2 may be switched directly while maintaining the line pressure PL. In this case, for example, an oil pressure switch is provided in each of the oil passages between the control valves 112 and 113 and the fail safe valves 114 and 115, and the oil passages of the control valves 112 and 113 are both opened when the oil pressure switches are both on. 5 is executed, and the brake abnormal time control routine of FIG. 5 is executed. When both of the hydraulic switches are off, it is determined that there is an abnormality in which the oil passages of the control valves 112 and 113 are both shut off. The brakes B1 and B2 may be switched by directly switching the oil passages of the control valves 112 and 113 while maintaining the line pressure PL.

  In the hybrid vehicle 20 of the embodiment, the power of the motor MG2 is changed by the transmission 60 and output to the ring gear shaft 32a. However, as illustrated in the hybrid vehicle 120 of the modified example of FIG. May be connected to an axle (an axle connected to wheels 39c and 39d in FIG. 10) different from an axle to which the ring gear shaft 32a is connected (an axle to which the drive wheels 39a and 39b are connected).

  In the hybrid vehicle 20 of the embodiment, the power of the engine 22 is output to the ring gear shaft 32a as the drive shaft connected to the drive wheels 39a and 39b via the power distribution and integration mechanism 30, but the modified example of FIG. The hybrid vehicle 220 includes an inner rotor 232 connected to the crankshaft 26 of the engine 22 and an outer rotor 234 connected to a drive shaft that outputs power to the drive wheels 39a and 39b. A counter-rotor motor 230 that transmits a part of the power to the drive shaft and converts the remaining power into electric power may be provided.

  In the embodiment, the present invention is applied to a hybrid vehicle that can output the power from the internal combustion engine and the power from the electric motor to the drive shaft. However, the present invention is not limited to such a hybrid vehicle. It can also be applied to electric vehicles. Further, a power output device that outputs the power from the internal combustion engine and the power from the electric motor to the drive shaft may be mounted on a vehicle other than an automobile, an aircraft, a ship, or the like. It is good also as a form of this control method.

  The embodiments of the present invention have been described using the embodiments. However, the present invention is not limited to these embodiments, and can be implemented in various forms without departing from the gist of the present invention. Of course you get.

1 is a configuration diagram showing an outline of the configuration of a hybrid vehicle 20 equipped with a power output device as one embodiment of the present invention. FIG. 3 is a configuration diagram showing an outline of a configuration of a transmission 60. 1 is a configuration diagram showing an outline of the configuration of a hydraulic circuit 100. FIG. It is explanatory drawing which shows an example of the action | operation of the fail safe valves 114 and 115. FIG. It is a flowchart which shows an example of the control routine at the time of the brake abnormality performed by the hybrid electronic control unit 70 of the hybrid vehicle 20 of an Example. It is a flowchart which shows an example of an electric pump drive control routine. It is a map which shows an example of the relationship between oil temperature To and fast fill time Tf. It is a map which shows an example of the relationship between oil temperature To and sweep gradient (DELTA) N. Time change of line pressure PL, duty ratios of linear solenoids 110 and 111, and target rotation speed Nopm of electric pump 104 when brake B1 is on and brake B2 is off and brakes B1 and B2 are both off. It is explanatory drawing which shows. FIG. 11 is a configuration diagram showing an outline of a configuration of a hybrid vehicle 120 according to a modification. FIG. 11 is a configuration diagram showing an outline of a configuration of a hybrid vehicle 220 of a modified example.

Explanation of symbols

20, 120, 220 Hybrid vehicle, 22 engine, 24 engine electronic control unit (engine ECU), 26 crankshaft, 28 damper, 30 power distribution integration mechanism, 31 sun gear, 32 ring gear, 32a ring gear shaft, 33 pinion gear, 34 carrier , 37 gear mechanism, 38 differential gear, 39a, 39b drive wheel, 39c, 39d wheel, 40 electronic control unit for motor (motor ECU), 41, 42 inverter, 43, 44 rotational position detection sensor, 50 battery, 52 for battery Electronic control unit (battery ECU), 54 power line, 60 transmission, 60a planetary gear mechanism of double pinion, 60b planetary gear mechanism of single pinion, 61 sun gear, 62 ring gear, 63a first pinion gear, 63b Second pinion gear, 64 carrier, 65 sun gear, 66 ring gear, 67 pinion gear, 68 carrier, 70 electronic control unit for hybrid, 72 CPU, 74 ROM, 76 RAM, 80 ignition switch, 81 shift lever, 82 shift position sensor, 83 accelerator Pedal, 84 Accelerator pedal position sensor, 85 Brake pedal, 86 Brake pedal position sensor, 88 Vehicle speed sensor, 100 Hydraulic circuit, 102 Mechanical pump, 103 Motor, 104 Electric pump, 105 3-way solenoid, 106 Pressure control valve, 108 Modulator Valve, 110, 111 Linear solenoid, 112, 113 Control valve, 114, 115 Fail-safe valve, 116, 117 Accum , 121 temperature sensor, 120, 122, 123 hydraulic switch, MG1, MG2 motor, B1, B2 brake.

Claims (14)

A power output device that outputs power to a drive shaft,
Power means capable of outputting power;
A plurality of clutches that are actuated by fluid pressure of the working fluid, with engagement of at least one of the plurality of clutches and disengagement of a clutch different from the clutch from the power means; Power transmission means capable of transmitting power to the drive shaft;
Fluid pressure generating means for generating fluid pressure;
Fluid pressure supply means capable of individually supplying the fluid pressure generated by the fluid pressure generation means to the plurality of clutch sides;
When fluid pressure is supplied only between the fluid pressure supply means and the plurality of clutches and only from the fluid pressure supply means to the engaged clutch side of the plurality of clutches, at least the fluid pressure on the clutch side When the fluid pressure is supplied from the fluid pressure supply means to the engaging clutch side of the plurality of clutches and the clutch side different from the clutch, Automatic opening / closing means for automatically interrupting the transmission of fluid pressure so that the engagement of the clutch is also released,
When an abnormality that releases the engagement of any of the plurality of clutches occurs, the fluid pressure generating means is controlled so that the fluid pressure is reduced, and after the fluid pressure is reduced, the plurality of clutches The fluid pressure supply means is arranged so that the supply of fluid pressure to the clutch side that can be engaged regardless of the abnormality is released and the supply of fluid pressure to another clutch different from the clutch is shut off. And controlling the fluid pressure generating means to control the fluid pressure generating means so that the engagement force acts on the clutch that can be engaged regardless of the abnormality by gradually increasing the fluid pressure after controlling the fluid pressure supply means. When,
A power output device comprising: The power output device according to claim 1,
The fluid pressure generating means includes a pumping means having an electric pumping means for pumping the working fluid using at least electric power,
The abnormal time control means controls the pressure feeding means so as to reduce the fluid pressure when an abnormality that releases the engagement of any of the plurality of clutches occurs, and reduces the fluid pressure. The supply of fluid pressure to the clutch side that can be engaged regardless of the abnormality among the plurality of clutches is released later, and the supply of fluid pressure to another clutch different from the clutch is shut off. The fluid pressure supply means is controlled, and after the fluid pressure supply means is controlled, the electric pressure feeding means is controlled so that the fluid pressure is gradually increased and the engagement force acts on the clutch that can be engaged regardless of the abnormality. Power output device that is means.   The power output apparatus according to claim 2, wherein the abnormal time control means is means for reducing fluid pressure by stopping operation of the pressure feeding means. The power output device according to claim 2 or 3,
Temperature detecting means for detecting the temperature of the working fluid pumped by the pumping means;
The abnormal-time control means is means for controlling the electric pumping means so that the fluid pressure is increased with a sweep gradient based on the detected temperature of the working fluid.   The power output apparatus according to claim 4, wherein the sweep gradient is a gradient set so as to increase as the detected temperature of the working fluid decreases.   The abnormal time control means controls the electric pumping means so that the preparation for applying the engaging force to the clutch that can be engaged regardless of the abnormality is executed for a predetermined time, and after the preparation is completed. The power output apparatus according to any one of claims 2 to 5, which is means for controlling the electric pressure feeding means so that an increase in engagement force of a clutch that can be engaged regardless of the abnormality is started. The power output device according to claim 6,
Temperature detecting means for detecting the temperature of the working fluid pumped by the pumping means;
The predetermined time is a time set based on the detected temperature of the working fluid.   The power output device according to claim 7, wherein the predetermined time is a time that is set to be longer as the detected temperature of the working fluid is lower.   The power output apparatus according to any one of claims 6 to 8, wherein the preparation is a fast fill that temporarily increases the amount of working fluid pumped from the electric pumping means.   The power output apparatus according to any one of claims 1 to 9, wherein the abnormal time control means is a means that functions while the drive shaft is rotating.   The power output apparatus according to claim 1, wherein the power means is an electric motor.   The power output device according to any one of claims 1 to 11, wherein the power transmission unit is a transmission unit that transmits power with a changeable gear ratio.   An automobile mounted with the power output device according to any one of claims 1 to 12 and having an axle connected to the drive shaft. Power means capable of outputting power, and a plurality of clutches operated by fluid pressure of the working fluid, and engagement of at least one of the plurality of clutches and disengagement of a clutch different from the clutch Power transmission means capable of transmitting power from the power means to the drive shaft, fluid pressure generation means for generating fluid pressure, and fluid pressure generated by the fluid pressure generation means to the plurality of clutch sides. Fluid pressure supply means that can be supplied individually, and fluid pressure is supplied only between the fluid pressure supply means and the clutch side to be engaged among the plurality of clutches, interposed between the fluid pressure supply means and the plurality of clutches. When this is done, at least the transmission of fluid pressure on the clutch side is automatically released, and the clutch side engaged with the clutches from the fluid pressure supply means is different from the clutch. An automatic opening / closing means for automatically interrupting transmission of fluid pressure so that engagement of any of the plurality of clutches is released when fluid pressure is supplied to the clutch side. A control method,
(A) controlling the fluid pressure generating means so that the fluid pressure is reduced when an abnormality that releases the engagement of any of the plurality of clutches occurs;
(B) After the fluid pressure is reduced, supply of fluid pressure to the clutch side that can be engaged regardless of the abnormality among the plurality of clutches is released, and to other clutches different from the clutch Controlling the fluid pressure supply means so that the supply of fluid pressure is interrupted;
(C) After controlling the fluid pressure supply means, the fluid pressure is gradually increased, and the fluid pressure generating means is controlled so that the engagement force acts on the clutch that can be engaged regardless of the abnormality. Control method.

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