JP2010143428A - Hydraulic control device of drive device for vehicle - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To adequately perform motor cooling, only when necessary. <P>SOLUTION: A hydraulic control device of a drive device for a vehicle, including a motor 20 for driving drive wheels, and a hydraulic connection/disconnection means 24 for connecting/disconnecting the motor 20 to/from the drive wheels, includes: an electric oil pump 50; an oil path 66 for controlling the connection/disconnection that supplies oil pressure for connection to the connection/disconnection means 24; an oil path 68 for cooling a motor that supplies working oil for cooling to the motor 20; and a means CVU for controlling and supplying working oil, disposed between a main oil path 62 on the discharge side of the electric oil pump 50 and the oil path 66 that controls connection/disconnection and the oil path 68 for cooling the motor, for blocking the main oil path 62 and the oil path 68 for cooling the motor and communicating the main oil path 62 and the oil path 66 that control connection/disconnection in a state where the main oil path 62 and the oil path 66 that control connection/disconnection are blocked, and for communicating the main oil path 62 and the oil path 68 for cooling the motor, in a state where the oil pressure for connection is supplied to the connection/disconnection means 24. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a hydraulic control device for a vehicle drive device including a drive motor, and belongs to the field of automobile drive technology.

  Conventionally, so-called hybrid vehicles are known in which a motor and an engine are mounted as drive sources, and drive wheels are driven by selectively using one of them. For example, a hybrid vehicle described in Patent Document 1 is configured such that a motor is connected or disconnected by a clutch with respect to a drive shaft that drives a drive wheel that is connected to an engine and an automatic transmission. Has been.

  When the motor is used as a drive source in this way, the motor receives a load from the drive wheel side and emits high heat to reach a high temperature state, and thus the motor needs to be cooled. Therefore, for example, as described in Patent Document 2, the motor is cooled by hydraulic oil supplied from an electric oil pump. Note that this electric oil pump supplies hydraulic oil not only for cooling the motor but also for lubrication to a predetermined lubrication point.

JP 2006-335190 A JP 2008-230281 A

  By the way, when cooling a high-temperature motor with hydraulic oil supplied from an electric oil pump, a method of always supplying hydraulic oil to the motor and a method of supplying hydraulic oil when the motor is in a high-temperature state You could think so. However, in the former case, hydraulic oil is supplied even when cooling of the motor is not necessary, and the electric oil pump consumes power wastefully. On the other hand, the latter requires a means for detecting whether or not the motor is in a high temperature state. In addition, when the electric oil pump supplies hydraulic oil in addition to the motor, the hydraulic control and the hydraulic system The configuration becomes complicated.

  Therefore, the present invention is equipped with a motor that drives the drive wheels via the intermittent means, and the motor oil supplied from the electric oil pump is used for a plurality of purposes such as hydraulic pressure and motor cooling. It is an object of the present invention to provide a hydraulic control device for a vehicle drive device that can be limited only when it is necessary to cool with hydraulic oil and that has a simple hydraulic control and hydraulic system configuration.

In order to solve the above-described problem, the invention according to claim 1 is directed to a hydraulic pressure of a vehicle drive device including a motor for driving a drive wheel and a hydraulic intermittent means for intermittently connecting the motor and the drive wheel. A control device,
An electric oil pump,
An intermittent control oil passage for supplying fastening hydraulic pressure to the intermittent means;
A motor cooling oil passage for supplying cooling hydraulic oil to the motor;
A state of being interposed between the main oil passage on the discharge side of the electric oil pump, the intermittent control oil passage and the motor cooling oil passage, and blocking the main oil passage and the intermittent control oil passage. Then, the main oil passage and the motor cooling oil passage are shut off, and the main oil passage and the motor are connected with the main oil passage and the intermittent control oil passage so that the fastening hydraulic pressure is supplied to the intermittent means. Hydraulic oil supply control means for communicating with the cooling oil passage is provided.

According to a second aspect of the present invention, in the hydraulic control device for a vehicle drive device according to the first aspect,
The hydraulic oil supply control means includes
A hydraulic pressure adjusting valve that adjusts the hydraulic pressure of the main oil passage and supplies the hydraulic pressure to the intermittent means;
The hydraulic pressure adjusted by the hydraulic pressure adjusting valve is supplied as a pilot pressure, and when the hydraulic pressure is equal to or higher than the hydraulic pressure for fastening the intermittent means, the switching valve is configured to communicate the main oil path with the motor cooling oil path. It is characterized by being.

Furthermore, the invention according to claim 3 is the hydraulic control device for the vehicle drive device according to claim 1,
The hydraulic oil supply control means includes
The main oil passage, the intermittent control oil passage and the motor cooling oil passage are shut off according to the supply or non-supply of the pilot pressure, and the main oil passage, the intermittent control oil passage and the motor cooling oil passage A switching valve for switching between the state and the communication state,
It is characterized by comprising an ON-OFF solenoid valve for controlling the supply or non-supply of the pilot pressure to the switching valve.

Furthermore, the invention according to claim 4 is the hydraulic control device for a vehicle drive device according to any one of claims 1 to 3,
The electric oil pump is configured such that the discharge amount of hydraulic oil can be adjusted.

In addition, the invention according to claim 5 is the hydraulic control device for a vehicle drive device according to any one of claims 1 to 4,
A lubricating oil passage that branches off from the main oil passage and supplies hydraulic oil to a predetermined lubricated location is provided,
The lubricating oil passage is provided with an orifice.

In addition, the invention according to claim 6 is the hydraulic control device for a vehicle drive device according to any one of claims 1 to 5,
A speed reduction means composed of a planetary gear set is provided between the motor and the intermittent means,
The intermittent means is constituted by a hydraulic brake for fixing a predetermined rotating element of the planetary gear set.

In addition, the invention according to claim 7 is the hydraulic control device for a vehicle drive device according to any one of claims 1 to 6,
A mechanical oil pump that is driven by the engine and supplies hydraulic oil to a predetermined location in the automatic transmission;
The main oil passage on the discharge side of the mechanical oil pump and the main oil passage on the discharge side of the electric oil pump are provided with a check valve for flowing hydraulic oil only from the latter oil passage to the former oil passage. It is connected by an oil passage.

  According to the first aspect of the invention, the main oil passage on the discharge side of the electric oil pump and the intermittent control oil passage for supplying the fastening hydraulic pressure to the intermittent means are interrupted by the hydraulic oil supply control means. In other words, when the intermittent means separates the motor and the drive wheels, the main oil passage and the motor cooling oil passage are shut off, assuming that the motor does not receive a load from the drive wheel and does not generate high heat. The hydraulic oil is not supplied from the electric oil pump to the motor.

  On the other hand, when the main oil passage and the intermittent control oil passage are communicated by the hydraulic oil supply control means, that is, when the intermittent means receives the supply of the fastening hydraulic pressure and connects the motor and the driving wheel. Assuming that the motor receives a load from the drive wheel side and generates high heat, the main oil passage and the motor cooling oil passage are communicated, and the hydraulic oil is supplied from the electric oil pump to the motor, and the motor operates Cooled by oil.

  With such simple control and configuration, hydraulic oil is supplied to the motor from the electric oil pump only when the motor needs to be cooled.

  According to the second aspect of the present invention, when the hydraulic pressure supplied to the intermittent means is adjusted to be higher than the hydraulic pressure at which the intermittent means connects the motor and the drive wheel by the hydraulic pressure adjusting valve, the adjusted hydraulic pressure is adjusted. The switching valve supplied with the pilot pressure communicates the main oil passage with the motor cooling oil passage. With such a simple configuration including the hydraulic pressure adjusting valve and the switching valve, the motor starts to cool after a while after the intermittent means connects the motor and the driving wheel. As a result, when the motor is in a low temperature state that does not require cooling immediately after connection, it is possible to prevent wasteful supply of hydraulic oil to the motor.

  According to the third aspect of the present invention, when the ON-OFF solenoid valve starts supplying the pilot pressure, the switching valve that receives the supply of the pilot pressure includes the main oil path, the intermittent control oil path, and the motor. Communicates with the cooling oil passage. With such a simple configuration comprising an ON-OFF solenoid valve and a switching valve, the hydraulic oil for fastening is supplied from the electric oil pump to the intermittent means, and at the same time, the hydraulic oil for cooling is supplied from the electric oil pump to the motor. The Thereby, since the temperature of the motor is high before it is connected to the drive wheels, the high temperature state is suppressed immediately after the connection.

  Furthermore, according to the invention described in claim 4, the electric oil pump is configured such that the discharge amount of the hydraulic oil can be adjusted. Thereby, the fastening and releasing operations of the intermittent means can be finely adjusted, and the connection and disconnection between the motor and the drive wheel can be smoothly performed while suppressing the shock.

  In addition, according to the fifth aspect of the present invention, there is provided a lubricating oil passage that branches off from the main oil passage and supplies hydraulic oil to a predetermined lubricated location, and the oil passage is provided with an orifice. The orifice suppresses the amount of hydraulic oil supplied to the lubricated portion from being more than necessary, and suppresses a decrease in hydraulic pressure supplied to the intermittent means. Further, the amount of hydraulic oil necessary for cooling is reliably supplied to the motor.

  In addition, according to the sixth aspect of the present invention, there is provided a speed reduction means composed of a planetary gear set between the motor and the intermittent means, and the intermittent means fixes the predetermined rotating element of the planetary gear set. It consists of a type brake. Thereby, a motor and a driving wheel can be reliably cut off with a simple configuration.

  If the intermittent means is constituted by a hydraulic clutch rather than a hydraulic brake, the intermittent means is caused by a centrifugal force acting on the residual hydraulic oil in the fastening hydraulic chamber in order to reliably disconnect the motor and the driving wheel. Therefore, the hydraulic clutch must have a more complicated structure than the hydraulic brake and provided with a centrifugal balance chamber.

  In addition, according to the invention described in claim 7, hydraulic oil is supplied from an electric oil pump from a mechanical oil pump provided in the automatic transmission and driven by an engine in the automatic variable transmission. The hydraulic oil is supplied to a predetermined location through a communication oil passage provided with a check valve that allows the hydraulic oil to flow only from the electric oil pump to the automatic transmission side. Thereby, even if the engine is stopped, the hydraulic oil is supplied to a predetermined location in the automatic transmission.

  Embodiments of the present invention will be described below.

(First embodiment)
FIG. 1 schematically shows the configuration of a hybrid vehicle according to a first embodiment of the present invention.

  A hybrid vehicle 10 shown in FIG. 1 includes an engine 12 as one drive source, a first motor 14 connected to the output shaft of the engine 12, an input shaft connected to the output shaft of the engine 12, and an output shaft. An automatic transmission 18 that is connected to the drive shaft 16 and is also a first connection / disconnection means for connecting / disconnecting the engine 12 and the drive shaft 16, a second motor 20 that is the other drive source, and a deceleration that decelerates the rotation of the motor 20. And a second intermittent means 24 for intermittently connecting the speed reducer 22 and the drive shaft 16. In addition, a battery 26 that supplies electric power to the first motor 14 and the second motor 20 is provided.

  When the engine 12 is selected as a drive source (for example, when the vehicle control device selects according to the traveling state or when the driver selects as the drive source), the automatic transmission 18, the drive shaft 16, the differential The drive wheel 32 is driven through the device 28 and the axle 30 in this order.

  The first motor 14 functions as a starter that receives power supplied from the battery 26 and cranks the engine 12. Further, during deceleration regeneration (especially when engine braking is used), the battery is driven by the drive wheel 32 through the drive shaft 16 to generate electric power and the battery 26 is charged.

  The automatic transmission 18 increases or decreases the rotation of the engine 12 according to the gear stage requested by the driver, or transmits the rotation to the drive shaft 16 as it is. Moreover, it functions as a connecting / disconnecting means for separating the engine 12 and the drive shaft 16 by entering the neutral state.

  When the second motor 20 is selected as a drive source, it receives power from the battery 26 and receives the reduction gear 22, the second intermittent means 24 in the engaged state (power transmission state), the drive shaft 16, and the differential device 28. The driving wheel 32 is driven through the axle 30 in order. Further, at the time of deceleration regeneration, it is driven by the drive wheel 32 via the drive shaft 16 and the like to generate electric power and charge the battery 26.

  Further, the second motor 20 is integrated with the speed reducer 22 and the second intermittent means 24 and is configured as a motor unit MU.

  FIG. 2 shows a partial cross-sectional view of the motor unit MU.

  In this motor unit MU, the speed reducer 22 is constituted by a planetary gear set including a sun gear 22a, a pinion 22b, a carrier 22c, and a ring gear 22d. Has been. The planetary gear set carrier 22 c is coupled to the output shaft 22 e of the speed reducer 22.

  Further, in the motor unit MU, the second intermittence means 24 is constituted by a hydraulic brake, and connects the ring gear 22d of the planetary gear set constituting the speed reducer 22 and the motor unit housing MUa so as to be connectable / disconnectable.

  In a state where the hydraulic brake constituting the second interrupting means 24 is supplied with hydraulic pressure and fastens the ring gear 22d to the motor unit housing MUa, the rotation of the sun gear 22a connected to the rotor 20a of the second motor 20 is pinion. The speed is reduced through 22b and transmitted to the carrier 22c, and the output shaft 22e of the speed reducer 22 connected to the carrier 22c rotates. Then, rotation (driving force) is transmitted to the driving wheel 32.

  On the other hand, in a state where the hydraulic brake constituting the second interrupting means 24 disconnects the ring gear 22d and the motor unit housing MUa, the rotation of the sun gear 22a connected to the rotor 20a of the second motor 20 is applied to the carrier 22c. Not transmitted but transmitted to the ring gear 22d via the pinion 22b. Then, the ring gear 22d rotates idly.

  Further, the motor unit MU, which will be described in detail later, is a control valve unit for cooling the second motor 20 and for supplying a fastening hydraulic pressure to a hydraulic brake constituting the second intermittent means 24 (claims). The CVU is attached.

  From here, the hydraulic system including the second motor 20 according to the present invention will be described.

  FIG. 3 schematically shows a hydraulic system that supplies hydraulic oil for cooling the second motor 20.

  This hydraulic system has an electric oil pump 50 as a hydraulic source, and includes a linear solenoid valve (corresponding to “hydraulic pressure regulating valve” described in the claims) 52 and a shift valve (claims) constituting the control valve unit CVU. In addition to cooling the second motor 20 with hydraulic fluid, the hydraulic pressure for constituting the second intermittent means 24 is supplied to the hydraulic brake, and It is configured to supply hydraulic oil as lubricating oil to a lubricated part 56 such as a gear, a shaft, or a bearing of the motor unit MU.

  The electric oil pump 50 is configured to take in the hydraulic oil stored in the oil pan 60 via the strainer 58 and discharge the taken hydraulic oil into the main oil passage 62. Further, the electric oil pump 50 is configured such that the discharge amount of the hydraulic oil can be adjusted, and the discharge amount is controlled by the controller 64.

  The linear solenoid valve 52 has an input port 52a connected to the main oil passage 62, adjusts the hydraulic pressure input via the input port 52a, and outputs the adjusted hydraulic pressure via the output port 52b. It is configured. The output port 52 b is connected to an intermittent control oil passage 66 that supplies a fastening hydraulic pressure to the second intermittent means (hydraulic brake) and supplies a pilot pressure to the shift valve 54.

  The linear solenoid valve 52 is configured to adjust the hydraulic pressure input via the input port 52a to the hydraulic pressure corresponding to the signal (current) sent from the controller 64 and output the hydraulic pressure via the output port 52b. ing. The output characteristics of the linear solenoid valve 52 are shown in FIG. As shown in FIG. 4, the input current I and the output pressure P have a linear relationship, and when the input current I becomes a high current, the output pressure P also becomes high.

  The shift valve 54 is configured such that its input port 54a is connected to the main oil passage 62, and the hydraulic fluid that flows in through the input port 54a is adjusted to flow out and flows out through the output port 54b. ing. The output port 54 b is connected to a motor cooling oil passage 68 that supplies hydraulic oil to the second motor 20 for cooling.

  Further, the shift valve 54 is provided with a pilot pressure port 54c that is connected to the intermittent control oil passage 66 and into which the hydraulic pressure adjusted by the linear solenoid valve 52 is input as a pilot pressure, and the pilot input to the port 54c. The hydraulic oil having a flow rate corresponding to the pressure is output from the output port 54b.

Specifically, as shown in the output characteristics of the shift valve 54 in FIG. 5, when the pilot pressure inputted to the pilot pressure port 54c is greater than P _0, begins communicates the input port 54a and output port 54b, it Thereafter, the shift valve 54 is configured so that the output flow rate increases when the pilot pressure becomes high. The hydraulic pressure P ₀ is set to be equal to or higher than the hydraulic pressure P _{B at which} the hydraulic brake constituting the second intermittent means 24 fastens the ring gear 22d of the planetary gear set to the motor unit housing MUa.

  The oil to be lubricated 56 is supplied with hydraulic oil from the electric oil pump 50 through a lubricating oil passage 70 branched from the main oil passage 62. The lubrication oil passage 70 is provided with an orifice 72 so that excessive hydraulic oil does not flow into the lubricated portion 56. The orifice 72 prevents the hydraulic pressure supplied to the second intermittent means 24 from being reduced below the minimum required hydraulic pressure, and ensures that the amount of hydraulic oil necessary for cooling is reliably supplied to the second motor 20. To be supplied.

  According to the hydraulic system shown in FIG. 3, when the electric oil pump 50 is started by the controller 64, the electric oil pump 50 starts to discharge the hydraulic oil stored in the oil pan 60 to the main oil passage 62. Then, hydraulic oil is supplied to the lubricated part 56 via the lubricating oil passage 70.

  Next, when the controller 64 inputs a signal (current) to the linear solenoid valve 52, the linear solenoid valve 52 connects the main oil passage 62 and the intermittent control oil passage 66, and the hydraulic pressure is supplied to the intermittent control oil passage 66. Begin to supply.

When the controller 64 increases the input current to the linear solenoid valve 52 from there, the hydraulic pressure in the intermittent control oil passage 66 is increased by the linear solenoid valve 52. When the hydraulic pressure reaches P _B , the hydraulic brake constituting the second intermittent means 24 fastens the ring gear 22d of the planetary gear set to the motor unit housing MUa, that is, the second motor 20 and the drive shaft 16 are connected. The

Further, when the controller 64 increases the input current to the linear solenoid valve 52, the hydraulic pressure in the intermittent control oil passage 66 exceeds P _B and increases to P ₀ by the linear solenoid valve 52. Then, the shift valve 54 receives the hydraulic pressure as a pilot pressure, and connects the main oil passage 62 and the motor cooling oil passage 68. Thereby, hydraulic oil is supplied to the 2nd motor 20, and the 2nd motor 20 begins to be cooled.

  According to this embodiment, the linear solenoid valve 52 and the shift valve 54 constituting the hydraulic oil supply control means (control valve unit CVU) are connected to the main oil passage 62 on the discharge side of the electric oil pump 54 and the second intermittent connection. In a state where the intermittent control oil passage 66 for supplying the engagement hydraulic pressure to the means (hydraulic brake) 24 is shut off, that is, when the second intermittent means 24 separates the second motor 20 and the drive shaft 16. Assuming that the second motor 20 does not receive a load from the drive shaft side and does not generate high heat, the main oil passage 62 and the motor cooling oil passage 68 are cut off, and the second motor 20 is connected to the electric oil pump 50 by Hydraulic fluid is not supplied.

  On the other hand, when the main oil passage 62 and the intermittent control oil passage 66 are communicated, that is, the second intermittent means 24 receives the supply of the fastening hydraulic pressure and connects the second motor 20 and the drive shaft 16. When the second motor 20 receives a load from the drive shaft side and generates high heat, the main oil passage 62 and the motor cooling oil passage 68 communicate with each other, and the second motor 20 is operated from the electric oil pump 50. Oil is supplied, and the second motor 20 is cooled by the hydraulic oil.

  With such simple control and configuration, the hydraulic oil is supplied from the electric oil pump 50 to the second motor 20 only when the second motor 20 needs to be cooled.

The hydraulic pressure supplied to the second intermittent means 24 is adjusted when the linear solenoid valve 52 adjusts the second intermittent means 24 to be equal to or higher than the hydraulic pressure P _B for fastening the second motor 20 and the drive shaft 16. The shift valve 54 supplied with the hydraulic pressure as the pilot pressure causes the main oil passage 62 and the motor cooling oil passage 68 to communicate with each other. Therefore, the second motor 20 starts to be cooled after the second intermittent means 24 connects the second motor 20 and the drive shaft 16 for a while. Thereby, when there is the 2nd motor 20 in the low temperature state which does not need cooling just after a connection, it is suppressed that hydraulic oil is supplied to the 2nd motor 20 wastefully.

  Further, since the speed reducer 22 is constituted by a planetary gear set, and the second intermittent means 24 is constituted by a hydraulic brake for fixing the ring gear 22d of the planetary gear set, the second motor 20 and the drive shaft 16 can be configured with a simple configuration. Can be reliably separated.

(Second Embodiment)
This embodiment is substantially the same as the first embodiment, but the control valve unit is different.

  As shown in FIG. 3, the control valve unit CVU of the first embodiment is composed of a linear solenoid valve 52 and a shift valve 54, whereas the control valve unit CVU2 of the present embodiment as shown in FIG. , An ON-OFF solenoid valve 152 and a shift valve 154. The remaining hydraulic system part is the same as in the first embodiment.

  The ON-OFF solenoid valve 152 is controlled by the controller 64 and is configured to communicate or block the main oil passage 62 and the pilot pressure supply oil passage 174 connected to the pilot pressure port 154a of the shift valve 154. Has been.

  The shift valve 154 includes two input ports 154b and 154c connected to the main oil passage 62. When the pilot pressure is input to the pilot pressure port 154a, the output port 154d communicated with the input port 154b; And an output port 154e communicated with the input port 154c. FIG. 6 shows a non-communication state, and FIG. 7 shows a communication state. The output port 154d is connected to the intermittent control oil passage 66, and the output port 154e is connected to the motor cooling oil passage 68.

  The pilot pressure supply oil passage 174 and the motor cooling oil passage 68 are provided with orifices 176 and 178.

  According to the hydraulic system shown in FIG. 6, when the electric oil pump 50 is started by the controller 64, the electric oil pump 50 starts to discharge the hydraulic oil stored in the oil pan 60 to the main oil passage 62. Then, the oil is supplied to the lubricated portion 56 via the lubricating oil passage 70.

  Next, when the controller 64 inputs an ON signal to the ON-OFF solenoid valve 152, the ON-OFF solenoid valve 152 communicates the main oil passage 62 and the pilot pressure supply oil passage 174.

  The ON-OFF solenoid valve 152 communicates the main oil passage 62 and the pilot pressure supply oil passage 174 at substantially the same time, whereby the shift valve 154 receives the supply of pilot pressure, and the main oil passage 62 and the intermittent control oil passage. 66 and the motor cooling oil passage 68 are communicated with each other. And the hydraulic brake which comprises the 2nd intermittent means 24 fastens the ring gear 22d of a planetary gear set to the motor unit housing MUa (refer FIG. 2), ie, the 2nd motor 20 and the drive shaft 16 are connected. At the same time, hydraulic oil is supplied to the second motor 20 and the second motor 20 starts to be cooled.

  According to the present embodiment, when the ON-OFF solenoid valve 152 starts supplying the pilot pressure, the shift valve 154 that has received the pilot pressure supplies the main oil path 62, the intermittent control oil path 66, and the motor cooling motor. The oil passage 68 is communicated. As a result, the fastening hydraulic pressure is supplied from the electric oil pump 50 to the second intermittent means 24, and at the same time, the cooling hydraulic oil is supplied from the electric oil pump 50 to the second motor 20. Thereby, since the temperature is high before the 2nd motor 20 is connected with the drive shaft 16, it will be suppressed that it will be in a high temperature state immediately after a connection.

  Although the present invention has been described with reference to the above-described two embodiments, the present invention is not limited to this.

  For example, the electric oil pump 50 may not be able to adjust the discharge amount of hydraulic oil. However, the one that can adjust the discharge amount of the hydraulic oil can finely adjust the fastening and releasing operation of the second intermittent means 24, and the connection between the second motor 20 and the drive shaft 16 while suppressing the shock. , Separation can be performed smoothly. In the case of the second embodiment, the hydraulic oil adjustment valve such as the linear solenoid valve that adjusts the oil pressure is not provided as in the first embodiment. Therefore, the electric oil pump has a hydraulic oil discharge amount of Adjustable ones are preferred.

  Further, in the above-described embodiment, the supply destination to which the electric oil pump 50 supplies the hydraulic oil is the second motor 20, the second intermittent means 24, and the lubricated portion 56, but is not limited thereto.

  For example, in the case of the first embodiment, as shown in FIG. 8, a mechanical oil pump 18 a provided in the automatic transmission 18 and driven by the engine 12 from the electric oil pump 50 in the automatic variable transmission 18. The hydraulic oil may be supplied to a friction element 18b such as a clutch or a brake, a torque converter 18c, and a lubricated portion 18d such as a shaft or a bearing to which the hydraulic oil is supplied. Thereby, even if the engine 20 is stopped, hydraulic oil is supplied to them.

  However, as shown in FIG. 8, the communication oil passage 282 that connects the main oil passage 62 and the discharge-side oil passage 18e of the mechanical oil pump 18a is operated only from the electric oil pump side to the automatic transmission side. It is necessary to provide a check valve 284 for flowing oil. As a result, the hydraulic oil discharged from the mechanical oil pump 18a flows to the electric oil pump side, and it is suppressed that the hydraulic pressure supplied to the friction element such as the clutch of the automatic transmission is insufficient.

  Furthermore, in the case of the above-mentioned embodiment, although the 2nd interruption means 24 is comprised with the hydraulic brake as shown in FIG. 2, you may comprise with a clutch. However, if the second interrupting means 24 is constituted by a hydraulic clutch, the second interrupting means 24 applies centrifugal force to the residual hydraulic oil in the fastening hydraulic chamber in order to reliably disconnect the second motor 20 and the drive shaft 16. In order to prevent unintentional fastening caused by doing this, the hydraulic clutch must have a more complicated structure than the hydraulic brake, provided with a centrifugal balance chamber.

  Finally, in the case of the above-described embodiment, the hybrid vehicle is provided with the engine 12 and the second motor 20 as drive sources, but is not limited thereto. The present invention can be implemented as long as the vehicle includes a motor for driving the drive wheels and hydraulic intermittent means for intermittently connecting the motor and the drive wheels.

  As described above, the present invention is provided in a vehicle in which a motor that drives a drive wheel via an intermittent means is mounted, and hydraulic oil supplied from an electric oil pump is used for a plurality of purposes such as hydraulic pressure and motor cooling. The cooling of the motor with hydraulic oil can be limited only when necessary, and the hydraulic control and the configuration of the hydraulic system for that can be simplified. Therefore, it may be suitably used in the field of vehicles using a motor as a drive source.

1 is a schematic configuration diagram of a hybrid vehicle according to a first embodiment of the present invention. It is a fragmentary sectional view of the motor unit MU of FIG. It is a figure showing roughly the hydraulic system concerning a 1st embodiment. It is a figure which shows the output characteristic of the linear solenoid valve shown in FIG. It is a figure which shows the output characteristic of the shift valve shown in FIG. It is a figure which shows roughly the hydraulic system which concerns on 2nd Embodiment. It is a figure which shows the connection state of the shift valve shown in FIG. It is a figure which shows schematically the hydraulic system of another embodiment.

Explanation of symbols

20 Motor (second motor)
24 Intermittent means (second intermittent means)
50 Electric oil pump 62 Main oil passage 66 Intermittent control oil passage 68 Motor cooling oil passage CVU Hydraulic oil supply control means (control valve unit)

Claims (7)

A hydraulic control device for a vehicle drive device, comprising: a motor for driving drive wheels; and a hydraulic intermittent means for intermittently connecting the motor and the drive wheels,
An electric oil pump,
An intermittent control oil passage for supplying fastening hydraulic pressure to the intermittent means;
A motor cooling oil passage for supplying cooling hydraulic oil to the motor;
A state of being interposed between the main oil passage on the discharge side of the electric oil pump, the intermittent control oil passage and the motor cooling oil passage, and blocking the main oil passage and the intermittent control oil passage. Then, the main oil passage and the motor cooling oil passage are shut off, and the main oil passage and the motor are connected with the main oil passage and the intermittent control oil passage so that the fastening hydraulic pressure is supplied to the intermittent means. A hydraulic control device for a vehicle drive device, comprising hydraulic fluid supply control means for communicating with a cooling oil passage. The hydraulic control device for a vehicle drive device according to claim 1,
The hydraulic oil supply control means includes
A hydraulic pressure adjusting valve that adjusts the hydraulic pressure of the main oil passage and supplies the hydraulic pressure to the intermittent means;
The hydraulic pressure adjusted by the hydraulic pressure adjusting valve is supplied as a pilot pressure, and when the hydraulic pressure is equal to or higher than the hydraulic pressure for fastening the intermittent means, the switching valve is configured to communicate the main oil path with the motor cooling oil path. A hydraulic control apparatus for a vehicle drive device. The hydraulic control device for a vehicle drive device according to claim 1,
The hydraulic oil supply control means includes
The main oil passage, the intermittent control oil passage and the motor cooling oil passage are shut off according to the supply or non-supply of the pilot pressure, and the main oil passage, the intermittent control oil passage and the motor cooling oil passage A switching valve for switching between the state and the communication state,
A hydraulic control device for a vehicle drive device, comprising: an ON-OFF solenoid valve that controls supply and non-supply of the pilot pressure to the switching valve. The hydraulic control device for a vehicle drive device according to any one of claims 1 to 3,
The electric oil pump is configured to be capable of adjusting a discharge amount of hydraulic oil, and is a hydraulic control device for a vehicle drive device. The hydraulic control device for a vehicle drive device according to any one of claims 1 to 4,
A lubricating oil passage that branches off from the main oil passage and supplies hydraulic oil to a predetermined lubricated location is provided,
A hydraulic control device for a vehicle drive device, wherein an orifice is provided in the lubricating oil passage. The hydraulic control device for a vehicle drive device according to any one of claims 1 to 5,
A speed reduction means composed of a planetary gear set is provided between the motor and the intermittent means,
The hydraulic control device for a vehicular drive device, wherein the intermittent means is constituted by a hydraulic brake that fixes a predetermined rotating element of the planetary gear set. The hydraulic control device for a vehicle drive device according to any one of claims 1 to 6,
A mechanical oil pump that is driven by the engine and supplies hydraulic oil to a predetermined location in the automatic transmission;
The main oil passage on the discharge side of the mechanical oil pump and the main oil passage on the discharge side of the electric oil pump are provided with a check valve for flowing hydraulic oil only from the latter oil passage to the former oil passage. A hydraulic control device for a vehicle drive device, wherein the hydraulic control device is connected by an oil passage.

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