JP2018044603A - Hydraulic circuit device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a hydraulic circuit device which can add a working fluid discharged from an electric oil pump at the high-discharge of a mechanical oil pump, and can easily perform the drive control of the electric oil pump.SOLUTION: In a hydraulic circuit device 10 having a mechanical oil pump 21 and an electric oil pump 22, and a supply oil passage 60 located at a downstream side of a discharge oil passage 51 in which a working fluid discharged from the mechanical oil pump circulates, the hydraulic circuit device comprises a first spool valve 30 which can switch a flow passage of the working fluid discharged from the electric oil pump between the two oil passages on the basis of hydraulic pressure which is generated by the mechanical oil pump. When the hydraulic pressure is high, the first spool valve is switched to a first oil passage for introducing the working fluid into the supply oil passage via the discharge oil passage, and when the hydraulic pressure is low, the first spool valve is switched to a second oil passage for introducing the working fluid into the supply oil passage not via the discharge oil passage.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a hydraulic circuit device, and more particularly, to a hydraulic circuit device including a mechanical oil pump and an electric oil pump.

  In recent years, a hydraulic circuit device including a mechanical oil pump driven by engine or wheel rotation and an electric oil pump driven by an electric motor in parallel has been used (for example, Patent Document 1).

  FIG. 7 is a hydraulic circuit diagram of a conventional hydraulic circuit device 110. The hydraulic circuit device 110 includes a mechanical oil pump 121 and an electric oil pump 122 that send hydraulic oil stored in the oil pan 120 to an oil passage. The mechanical oil pump 121 and the electric oil pump 122 are arranged in parallel, and hydraulic oil discharged from these oil pumps 121 and 122 is supplied to a supply oil passage 160 in which the motor generator 126 and the gear mechanism 128 are arranged. be introduced.

  A check valve 124 is disposed on an oil passage 154 connecting the oil pumps 121 and 122 in parallel, and the check valve 124 is connected to the mechanical oil pump 121 from the electric oil pump 121 side. The backflow of the hydraulic oil to the 122 side is prevented.

  A relief valve 123 is disposed between the electric oil pump 122 and the check valve 124. The relief valve 123 opens the relief valve 123 when the discharge amount from the mechanical oil pump 121 is relatively large (hereinafter referred to as high discharge of the mechanical oil pump), so that the electric oil pump The oil pressure on the output side during the 122 drive is prevented from increasing.

  In the conventional hydraulic circuit device 110, when the oil pumps 121 and 122 are arranged in parallel, when the discharge amount from the mechanical oil pump 121 is relatively small (hereinafter referred to as low discharge of the mechanical oil pump). The amount of hydraulic oil supplied to the motor generator 126 and the gear mechanism 128 by driving the electric oil pump 122 is ensured. On the other hand, at the time of high discharge of the mechanical oil pump 121, the motor generator 126 and the gear mechanism 128 are lubricated and cooled only by supplying hydraulic oil discharged from the mechanical oil pump 121.

JP 2010-249205 A

  As described above, in the conventional hydraulic circuit device 110, hydraulic oil discharged from the electric oil pump 122 is added and supplied to the motor generator 126 and the gear mechanism 128 at the time of high discharge of the mechanical oil pump 121. Can not. Therefore, even when the mechanical oil pump 121 is at a high discharge and the motor generator 126 is at a high temperature, for example, when it is desired to increase the supply amount of hydraulic oil, this cannot be handled. It was.

  Further, when the hydraulic oil discharged by driving the electric oil pump 122 continues to be relieved at the time of high discharge of the mechanical oil pump 121, the battery continues to be consumed. On the other hand, if the drive amount of the electric oil pump 122 is controlled in accordance with the discharge amount from the mechanical oil pump 121 in order to avoid such wasteful consumption of the battery, the drive control of the electric oil pump 122 is complicated. Become.

  The present invention has been made in view of the above-described problem, and at the time of high discharge of a mechanical oil pump, the amount of hydraulic oil supplied can be increased by adding hydraulic oil discharged from the electric oil pump. Another object of the present invention is to provide a hydraulic circuit device that can easily perform drive control of an electric oil pump.

  In order to achieve the above object, a hydraulic circuit device according to claim 1 includes a mechanical oil pump and an electric oil pump arranged in parallel, and a discharge through which hydraulic oil discharged from the mechanical oil pump flows. In the hydraulic circuit device that is located downstream of the oil passage and includes a supply oil passage that supplies hydraulic oil to the gear mechanism and the motor generator, the electric oil is generated based on the hydraulic pressure generated by the mechanical oil pump. A first spool valve capable of switching the flow path of the hydraulic oil discharged from the pump between the two oil passages is provided via the discharge oil passage when the hydraulic pressure is high. When the hydraulic oil discharged from the electric oil pump is switched to the first oil passage for introducing the hydraulic oil into the supply oil passage and the oil pressure is low, the electric oil pump is not connected to the discharge oil passage. The discharged hydraulic oil, characterized in that it is switched to the second oil passage for introducing into said oil supply passage.

  According to this configuration, when the hydraulic pressure generated by the mechanical oil pump is high, that is, at the time of high discharge of the mechanical oil pump, the hydraulic oil discharged from the mechanical oil pump is supplied through the discharge oil passage. The hydraulic oil discharged from the electric oil pump can be introduced into the supply oil passage without going through the discharge oil passage. As a result, when the mechanical oil pump is discharged at high discharge, the hydraulic oil discharged from the electric oil pump can be added and supplied to the gear mechanism or the motor generator. Further, when the mechanical oil pump is discharged at a low rate, the hydraulic oil discharged from the electric oil pump can be introduced into the supply oil passage through the discharge oil passage and supplied to the gear mechanism and the motor generator.

  In addition, since it is possible to drive the electric oil pump while avoiding wasteful battery consumption at the time of high discharge of the mechanical oil pump, the complexity of the electric oil pump according to the discharge amount from the mechanical oil pump is reduced. Drive control can be eliminated, and drive control of the electric oil pump can be simplified.

  The invention according to claim 2 is the hydraulic circuit device according to claim 1, wherein the hydraulic oil is discharged from the mechanical oil pump based on the hydraulic pressure of the second oil passage generated by the electric oil pump. A second spool valve that switches the flow path of the hydraulic oil is provided.

  According to this configuration, at the time of high discharge of the mechanical oil pump in which the second oil passage is selected, based on the hydraulic pressure by the electric oil pump, that is, according to the amount of hydraulic oil discharged from the electric oil pump, The flow path of the hydraulic oil discharged from the mechanical oil pump can be switched. As a result, the amount of hydraulic oil supplied to the gear mechanism and the motor generator can be controlled more precisely according to the amount of hydraulic oil discharged from each oil pump, and the lubrication and cooling action by the hydraulic oil can be improved. Can do.

  According to a third aspect of the present invention, in the hydraulic circuit device according to the second aspect, the supply oil path includes a first supply oil path that supplies hydraulic oil to the gear mechanism, and an oil cooler. A second supply oil passage for supplying hydraulic oil to the motor generator, and the second spool valve is discharged from the mechanical oil pump when the hydraulic pressure in the second oil passage is lower than a predetermined value. When the hydraulic oil is switched to the first state in which the hydraulic oil can be introduced into the first supply oil passage and the second supply oil passage, and the hydraulic pressure of the second oil passage is higher than the predetermined value, the electric oil pump The discharged hydraulic oil is introduced into the first supply oil passage, and the operation oil is switched to a second state in which the hydraulic oil discharged from the mechanical oil pump is introduced into the second supply oil passage.

  According to this configuration, at the time of high discharge of the mechanical oil pump in which the second oil passage is selected and at the time of high discharge of the electric oil pump in which the hydraulic pressure of the second oil passage becomes high, the mechanical oil pump The discharged hydraulic oil can be cooled by the oil cooler and supplied to the motor generator, and the relatively high temperature hydraulic oil discharged from the electric oil pump can be supplied to the gear mechanism. Thereby, the cooling effect of the motor generator can be enhanced. In addition, when the mechanical oil pump is at high discharge and when the electric oil pump is low in discharge, the hydraulic oil discharged from the mechanical oil pump is transferred to the gear mechanism and the motor generator. Can be supplied.

  According to a fourth aspect of the present invention, in the hydraulic circuit device according to any one of the first to third aspects, the mechanical oil pump is interlocked with an output shaft that transmits a driving force of a vehicle engine to wheels. And a controller that controls the discharge amount of the electric oil pump based on the vehicle speed, the engine speed, and the temperature of the motor generator.

  According to this configuration, the drive control of the electric oil pump can be easily performed as compared with the case where the drive of the electric oil pump is controlled according to the discharge amount of the mechanical oil pump. Furthermore, since the discharge amount from the electric oil pump can be increased or decreased according to the temperature of the motor generator, when the motor generator needs to be cooled, the discharge amount of the electric oil pump can be increased to the supply oil passage. The amount of hydraulic oil introduced can be increased and the cooling effect of the motor generator can be enhanced.

  According to the hydraulic circuit device of the present invention, hydraulic oil discharged from the electric oil pump can be supplied to a gear mechanism or the like at the time of high discharge of the mechanical oil pump, and the supply amount of hydraulic oil can be increased. . In addition, the drive control of the electric oil pump can be easily performed.

1 is a hydraulic circuit diagram of a hydraulic circuit device according to an embodiment of the present invention. The block diagram which shows the drive control mechanism of the electric oil pump in a hydraulic circuit apparatus. It is a schematic diagram of the map which prescribes | regulates the relationship between the temperature of a motor generator, and the rotation speed of an electric oil pump, (a) shows a 1st map, (b) shows a 2nd map, (c) shows the 1st map. 3 maps are shown. The flowchart figure which shows operation | movement of a control unit. The figure explaining the flow of the hydraulic fluid of the hydraulic circuit apparatus shown in FIG. The figure explaining the flow of the hydraulic fluid of the hydraulic circuit apparatus shown in FIG. The figure which shows the conventional hydraulic circuit apparatus.

  FIG. 1 is a hydraulic circuit diagram of a hydraulic circuit device 10 according to an embodiment of the present invention. The hydraulic circuit device 10 is used in a vehicle equipped with an engine, and supplies hydraulic oil for lubrication and cooling to a drive mechanism of the vehicle. The hydraulic circuit device 10 includes an oil pan 20 that stores hydraulic oil, a mechanical oil pump 21 (hereinafter referred to as MOP 21) and an electric oil pump 22 (hereinafter referred to as “MOP 21”) that sends the hydraulic oil stored in the oil pan 20 to the oil passage. EOP22). The hydraulic oil discharged from the MOP 21 and the EOP 22 is returned to the oil pan 21 through the supply oil passage 60 where the motor generator 26 and the gear mechanism 28 are arranged. Supply oil path 60 has a first supply oil path 63 in which gear mechanism 28 is disposed and a second supply oil path in which motor generator 26 is disposed. A first spool valve 30 is disposed downstream of the EOP 22, and a second spool valve 40 is disposed downstream of the MOP 21.

  The motor generator 26 functions as an electric motor or a generator, and constitutes a part of a vehicle drive mechanism. The gear mechanism 28 includes a gear train that transmits the driving force from the engine and the motor generator for traveling to the wheels, and a bearing that supports the rotation shaft of these gears. For example, a planetary gear train that constitutes the drive mechanism of the vehicle, etc. Is included.

  The MOP 21 is an oil pump that is mechanically connected to an output shaft (not shown) that is connected to an engine and a motor generator for traveling to transmit driving force, and is rotationally driven by torque transmitted from the output shaft side. It is. Specifically, the rotor of the MOP 21 is configured to rotate in conjunction with the output shaft. For example, even when the engine is stopped, the vehicle is running and the output shaft is rotating. Then, the MOP 21 is rotationally driven. The output performance of MOP21 is higher than that of EOP22.

  The EOP 22 is connected to an electric motor (not shown), and is an oil pump that can be rotationally driven at an arbitrary timing independently of the MOP 21 by the electric motor. The EOP 22 and the MOP 21 are arranged in parallel in the hydraulic circuit.

  The hydraulic oil discharged from the MOP 21 flows out to the first discharge oil passage (discharge oil passage) 51, and the hydraulic oil discharged from the EOP 22 flows out to the second discharge oil passage 52. The second discharge oil passage 52 is connected to the first discharge oil passage 51 via the first spool valve 30 and the oil passage 54 connected to the first spool valve 30.

  The check valve 24 is disposed in the oil passage 54. The check valve 24 prevents the backflow of hydraulic oil from the first discharge oil passage 51 side to the first spool valve 30 side.

  The first spool valve 30 switches the flow path of the hydraulic oil discharged from the EOP 22 to the oil path (first oil path) 54 or the oil path (second oil path) 55 based on the hydraulic pressure generated by the MOP 21. The first spool valve 30 is inserted into the sleeve 31 so as to be movable in the linear direction, and is disposed on the one end 32a side of the spool 32 in the sleeve 31 to urge the spool 32 toward the other end 32b. A first spring (not shown). The sleeve 31 has an input port 31a to which hydraulic oil is supplied, and a first output port 31b and a second output port 31c that discharge hydraulic oil flowing in from the input port 31a. An oil chamber 31d is provided.

  The input port 31 a is connected to the downstream end of the second discharge oil passage 52. The first output port 31 b is connected to an oil passage 54 that joins the hydraulic oil discharged from the EOP 22 to the first discharge oil passage 51. The second output port 31 c is connected to the upstream end of the oil passage 55. The downstream end of the oil passage 55 is connected to the first supply oil passage 61 on the upstream side of the gear mechanism 28.

  A check valve 25 is disposed in the oil passage 55, and the check valve 25 prevents backflow of hydraulic oil from the first supply oil passage 61 side to the first spool valve 30 side.

A discharge pressure PM from the MOP 21 (that is, a hydraulic pressure generated by the MOP 21) acts on the oil chamber 31d. First spring, when the discharge pressure PM predetermined value PM ₀ greater than the high-pressure state, to move to one end 32a side spool 32 against the biasing force of the first spring, the discharge pressure PM predetermined value PM _{In a} low pressure state smaller than ₀ , the spool 32 is appropriately set so as to move to the other end 32b side by the biasing force of the first spring. When the discharge pressure PM is in the high pressure state, the hydraulic oil can flow between the input port 31a and the first output port 31b, and the discharge of the hydraulic oil from the second output port 31c is stopped. On the other hand, when the discharge pressure PM is in a low pressure state, the hydraulic oil can flow between the input port 31a and the second output port 31c, and the discharge of the hydraulic oil from the first output port 31b is stopped.

  The first discharge oil passage 51 is branched into two oil passages downstream of the junction 54 a with the oil passage 54. One branched oil passage 63 is connected to the first supply oil passage 61 via the second spool valve 40. The other branched oil passage constitutes a second supply oil passage 62 in which the motor generator 26 is disposed. An oil cooler 27 that cools hydraulic oil is disposed upstream of the motor generator 26 in the second supply oil passage 62.

  The second spool valve 40 switches the flow path of the hydraulic oil discharged from the MOP 21 based on the hydraulic pressure generated by the EOP 22. The second spool valve 40 is inserted into the sleeve 41 so as to be movable in a linear direction, and is disposed on the one end 42a side of the spool 42 in the sleeve 41 to urge the spool 42 toward the other end 42b side. A second spring (not shown). The sleeve 41 has an input port 41a to which hydraulic oil is supplied, and an output port 41b for discharging hydraulic oil flowing in from the input port 41a, and has an oil chamber 41c on the other end 42b side of the spool 42.

  The input port 41 a is connected to the downstream end of the oil passage 63, and the output port 41 b is connected to the upstream end of the first supply oil passage 61.

A discharge pressure PE from the EOP 22 (that is, a hydraulic pressure generated by the EOP 22) acts on the oil chamber 41c via the oil passage 55. In the second spring, when the discharge pressure PE is higher than the predetermined value PE ₀ , the spool 42 moves toward the one end 42a against the urging force of the second spring, and the discharge pressure PE is equal to the predetermined value PE. _{In a} low pressure state smaller than ₀ , the spool 42 is appropriately set so as to move to the other end 42b side by the biasing force of the second spring. When the discharge pressure PE is in a low pressure state, the operation state is switched to the first state in which the hydraulic oil can flow between the input port 41a and the output port 41b. When the discharge pressure PE is in a low pressure state, the spool 42 is switched to the second state in which the output port 42b is closed. In the second state, the discharge of hydraulic oil from the output port 41b is stopped.

  The hydraulic oil that has passed through the motor generator 26 and the hydraulic oil that has passed through the gear mechanism 28 are returned to the oil pan 20 through the oil passage 64 disposed on the downstream side thereof.

  Next, drive control of the EOP 22 will be described. In the present embodiment, the EOP 22 is driven and controlled based on the engine speed, the speed of its own vehicle, and the temperature of the motor generator 26. FIG. 2 is a block diagram showing the drive control mechanism 70 of the EOP 22 in the hydraulic circuit device 10. In addition to EOP 22, drive control mechanism 70 includes engine speed sensor 71, vehicle speed sensor 72 that detects the speed of the vehicle, temperature sensor 74 that detects the temperature of motor generator 26, and control unit (control unit) 76. including.

  The control unit 76 is constituted by a microcomputer including a central processing unit (CPU), a ROM storing programs, a ROM as a work area, and the like. The control unit 76 discharges from the EOP 22 based on the engine speed detected by the engine speed sensor 71, the vehicle speed detected by the vehicle speed sensor 72, and the temperature of the motor generator 26 detected by the temperature sensor 74. Control the amount. Specifically, the discharge amount is controlled to increase or decrease by controlling the rotation speed of the EOP 22 based on detection signals from the engine speed sensor 71, the vehicle speed sensor 72, and the temperature sensor 74.

The control unit 76 is set with a speed threshold value V ₁ and an engine speed threshold value Ne ₁ , Ne ₂ (Ne ₁ <Ne ₂ ) for determining the speed state of the MOP 21. The control unit 76 is preset with a map that defines the relationship between the rotational speed of the EOP 22 and the temperature of the motor generator 26 according to the vehicle speed V. In the present embodiment, the first to third maps are set according to the vehicle speed V as shown in FIGS. In FIG. 3, the vertical axis represents the rotation speed of the EOP 22, and the horizontal axis represents the temperature of the motor generator 26. Note that the magnitude relationship of the temperature T in each map is T ₀ ≦ T ₂ <T ₄ .

As shown in FIG. 3 (a), in the first map, the rotation speed n of the EOP 22 is determined based on the predetermined temperatures T ₀ and T ₁ defined in advance for the temperature T of the motor generator 26. It is controlled to be n ₁ and n ₂ . Specifically, when the temperature T is less than T ₀ , the rotational speed n becomes zero (that is, the EOP 22 stops driving), and when the temperature T is T ₀ ≦ T <T ₁ , the rotational speed n ₁ (that is, EOP 22 low ejection state) ejection amount is small from the temperature T is the rotational speed n _{2 (i.e.,} when the above T ₁ is controlled to be high ejection state) ejection amount is large from EOP22.

As shown in FIG. 3B, in the second map, control is performed so that the rotational speed n of the EOP 22 becomes the rotational speeds n ₁ and n ₂ with reference to predetermined temperatures T ₂ and T ₃ defined in advance for the temperature T. Is done. Specifically, when the temperature T is less than T ₂ , the rotation speed n is zero, and when the temperature T is T ₂ ≦ T <T ₃ , the rotation speed n ₁ (low discharge state) is obtained, and the temperature T is T _3. At this time, the rotation speed is controlled to be n ₂ (high discharge state).

As shown in FIG. 3 (c), in the third map, it is controlled so that the rotational speed n of EOP22 a predetermined temperature T ₄ the temperature T of the motor generator 26 is previously defined as a reference becomes the rotational speed n ₂ . Specifically, the rotational speed n becomes zero when less than the temperature T is T _4, is controlled so that the temperature T is the rotational speed n _{2 (high} ejection state) when T ₄ or higher.

In addition, the two-dot chain line in the 1st map of FIG. 3 and the 2nd map has shown the example of a change of the relationship between the temperature T and the rotation speed n. In the modified example, when the EOP 22 is changed from the low discharge state to the high discharge state or from the high discharge state to the low discharge state according to the temperature T, the rotation speed n is controlled to be gradually increased or decreased. In this case, a state where the rotational speed n is 0 <n <n ₂ can be a low discharge state, and a state where the rotational speed n is n ≧ n ₂ can be a high discharge state.

  FIG. 4 is a flowchart showing the operation of the control unit 76. Hereinafter, the processing of the control unit 76 will be described step by step.

First, the control unit 76 determines from the detection signals from the engine speed sensor 71 and the vehicle speed sensor 72 whether the vehicle speed V is less than zero and the engine speed Ne is less than the threshold value Ne ₁ (step S101). When the vehicle speed V is less than zero and the engine speed Ne is less than the threshold value Ne ₁ (that is, when the vehicle is in a reverse state) (step S101: Yes), the control unit 76 refers to the first map, and the temperature sensor Based on the detection signal from 74, the rotational speed n of the EOP 22 is determined from the temperature T of the motor generator 26, and the EOP 22 is driven and controlled to be the determined rotational speed n (step S102).

Vehicle speed V is zero or more, or, when the engine speed Ne is the threshold value Ne ₁ or more (step S101: No), whether the vehicle speed V is the speed threshold _{V 1} or more, or, the engine speed Ne is the threshold value Ne ₂ or more (Step S103). Vehicle speed V is not the threshold value _{V 1} or more, i.e., the vehicle speed V is 0 ≦ V _{<V 1,} and when the engine speed Ne is Ne <Ne _2, or a vehicle speed V is V <0, and the engine When the rotational speed Ne is Ne ₁ ≦ Ne <Ne ₂ (step S103: No), the control unit 76 refers to the second map, and based on the detection signal from the temperature sensor 74, the temperature T of the motor generator 26 is EOP22. And the EOP 22 is driven and controlled so as to be the determined rotation speed n (step S104).

The vehicle speed V is the threshold value _{V 1} above, or, when the engine speed Ne is the threshold value Ne ₂ or more (step S103: Yes), the control unit 76 refers to the third map, the detection signal from the temperature sensor 74 Based on the temperature T of the motor generator 26, the rotational speed n of the EOP 22 is determined, and the EOP 22 is driven and controlled to achieve the determined rotational speed n (step S105).

The vehicle speed V is a threshold value _{V 1} above, or, when the engine speed Ne is the threshold Ne ₂ or more high-speed running state, becomes higher rotational speed of MOP21, a high discharge state discharge amount is increased from MOP21. Therefore, when the high discharge of MOP21, EOP22 either stopped rotational speed is zero, (consisting i.e. the rotational speed n ₂₎ speed is high becomes high ejection state.

  Next, the flow of the hydraulic oil in the hydraulic circuit device 10 described above will be described with reference to FIGS. In each figure, the arrows described along the oil passage indicate the flow of hydraulic oil. FIG. 1 shows the flow of hydraulic oil at the time of low discharge of MOP21, FIG. 5 shows the case of high discharge of MOP21 and EOP22 in a stopped state, and FIG. 6 shows the time of high discharge of MOP21. The case where EOP22 is in a high discharge state is shown. 1, 5 and 6, the positions of the spools 32 and 42 of the first and second spool valves 30 and 40 are different. Here, for convenience, the state shown in FIG. 1 is the first circuit state and FIG. The state shown is the second circuit state, and the state shown in FIG. 6 is the third circuit state.

  First, the first circuit state will be described. The hydraulic oil discharged from the MOP 21 flows into the first discharge oil passage 51, and the first spool valve 30 discharges the hydraulic oil from the first output port 31b when the discharge pressure PM from the MOP 21 is in a low pressure state. Can be switched. As a result, the hydraulic oil discharged from the EOP 22 flows into the first discharge oil passage 51 via the oil passage 54 and merges with the hydraulic oil discharged from the MOP2.

  The second spool valve 40 is in a first state in which the hydraulic oil can flow when the discharge of the hydraulic oil to the oil passage 55 is stopped and the discharge pressure PE from the EOP 22 becomes a low pressure state. Accordingly, a part of the hydraulic oil passing through the first discharge oil passage 51 is supplied to the gear mechanism 28 through the oil passage 63, the second spool valve 40, and the first supply oil passage 61. The remaining hydraulic oil that passes through the first discharge oil passage 51 passes through the second supply oil passage 62, is cooled by the oil cooler 27, and then is supplied to the motor generator 26. The hydraulic oil supplied to the gear mechanism 28 and the motor generator 26 is returned to the oil pan 20 through the oil passage 64.

  As described above, when the MOP 21 is discharged at a low rate (including the case where the discharge amount from the MOP 21 is zero), the discharge pressure PE is in a low pressure state, so the EOP 22 is in a low discharge state (the discharge amount from the EOP 22 is zero). 1) and the high discharge state. When the discharge amount from the MOP 21 is zero, the hydraulic oil discharged from the EOP 22 is supplied to the motor generator 26 and the gear mechanism 28.

  Next, the second circuit state will be described. The hydraulic oil discharged from the MOP 21 flows into the first discharge oil passage 51, and the first spool valve 30 discharges the hydraulic oil from the second output port 31c when the discharge pressure PM of the MOP 21 becomes a high pressure state. Are switched as follows. As a result, the hydraulic oil discharged from the EOP 22 can flow into the oil passage 55, but the EOP 22 is in a stopped state in the second circuit state.

  The second spool valve 40 is in a first state in which hydraulic fluid can flow when the EOP 22 is in a stopped state and the discharge pressure PE is in a low pressure state. Accordingly, a part of the hydraulic oil passing through the first discharge oil passage 51 is supplied to the gear mechanism 28 through the oil passage 63, the second spool valve 40, and the first supply oil passage 61. The remaining hydraulic oil that passes through the first discharge oil passage 51 passes through the second supply oil passage 62, is cooled by the oil cooler 27, and then is supplied to the motor generator 26. The hydraulic oil supplied to the gear mechanism 28 and the motor generator 26 is returned to the oil pan 20 through the oil passage 64.

  Next, the third circuit state will be described. The hydraulic oil discharged from the MOP 21 flows into the first discharge oil passage 51, and the first spool valve 30 causes the hydraulic oil to be discharged from the second output port 31c when the discharge pressure PM becomes a high pressure state. Switched. As a result, the hydraulic oil discharged from the EOP 22 flows into the oil passage 55.

  The second spool valve 40 is in a second state in which the discharge of hydraulic oil from the output port 41b is stopped when the EOP 22 is in a high discharge state and the discharge pressure PE is in a high pressure state. As a result, the hydraulic oil discharged from the MOP 21 passes through the first discharge oil passage 51 and the second supply oil passage 62, is cooled by the oil cooler 27, and then is supplied to the motor generator 26. Further, the hydraulic oil discharged from the EOP 22 is supplied to the gear mechanism 28 through the oil passage 55 and the first supply oil passage 61. The hydraulic oil supplied to the gear mechanism 28 and the motor generator 26 is returned to the oil pan 20 through the oil passage 64.

  In the hydraulic circuit device 10 described above, the hydraulic oil discharged from the EOP 22 can be added together with the hydraulic oil discharged from the MOP 21 and supplied to the gear mechanism 28 and the motor generator 26 when the MOP 21 is discharged at a high rate. The hydraulic oil supply amount can be increased as compared with the hydraulic circuit device.

  Further, the complicated drive control of the EOP 22 according to the discharge amount from the MOP 21 can be eliminated, and the drive control of the EOP 22 can be easily performed. In particular, since the EOP 22 can be driven and controlled based on the vehicle speed V and the temperature Y of the motor generator 26, the drive control of the EOP 21 is simple. Further, since the discharge amount from the EOP 22 can be increased or decreased according to the temperature of the motor generator 26, when the motor generator 26 needs to be cooled, the amount of hydraulic oil supplied to the hydraulic circuit is increased and the cooling is performed. The effect can be enhanced.

  Further, when the MOP 21 is discharged at a high rate, the flow of hydraulic oil discharged from the MOP 21 is switched by the discharge pressure PE from the EOP 22 to finely control the amount of hydraulic oil supplied to the gear mechanism 28 and the motor generator 26. Can do.

  Specifically, in the second circuit state in which the EOP 22 is stopped, the hydraulic oil discharged from the MOP 21 can be supplied to the motor generator 26 and the gear mechanism 28. On the other hand, in the third circuit state in which the EOP 22 is in a high discharge state, all of the relatively high temperature hydraulic oil discharged from the EOP 22 is supplied to the gear mechanism 28, and a large amount of hydraulic oil discharged from the MOP 21 is cooled to all motors. The generator 26 can be supplied. Therefore, when the temperature T of the motor generator 26 is high, it can be cooled by a low temperature and a large amount of hydraulic oil, and the cooling effect is high.

  In addition, this invention is not limited to embodiment mentioned above, A various change is possible in the range which does not deviate from the meaning of invention. For example, in the above-described embodiment, the two spool valves 30 and 40 for switching the flow path are provided in the hydraulic circuit device 10, but a configuration in which only the first spool valve 30 is provided may be employed. The vehicle speed and the engine speed use values detected by the vehicle speed sensor 72 and the engine speed sensor 71, but the motor generator 126 and the rotation speed of the output shaft are directly or indirectly determined by using other values. A value calculated or estimated may be used.

DESCRIPTION OF SYMBOLS 10 Hydraulic circuit apparatus 20 Oil pan 21 Mechanical oil pump 22 Electric oil pump 26 Motor generator 28 Gear mechanism 30 1st spool valve 40 2nd spool valve 51 1st discharge oil path (discharge oil path)
54 Oil passage (first oil passage)
55 Oil passage (second oil passage)
Reference Signs List 60 oil supply path 61 first oil supply path 62 second oil supply path 70 drive control mechanism 71 engine speed sensor 72 vehicle speed sensor 74 temperature sensor 76 control unit (control unit)

Claims (4)

A mechanical oil pump and an electric oil pump arranged in parallel;
In a hydraulic circuit device including a supply oil passage that is located downstream of a discharge oil passage through which hydraulic oil discharged from the mechanical oil pump flows and supplies the hydraulic oil to a gear mechanism and a motor generator,
A first spool valve capable of switching a flow path of hydraulic oil discharged from the electric oil pump between two oil paths based on a hydraulic pressure generated by the mechanical oil pump;
The first spool valve is
When the oil pressure is high, the hydraulic oil discharged from the electric oil pump is switched to the first oil passage through the discharge oil passage to the supply oil passage,
When the oil pressure is low, the oil pressure is switched to the second oil passage for introducing the hydraulic oil discharged from the electric oil pump into the supply oil passage without going through the discharge oil passage. Circuit device.   2. A second spool valve that switches a flow path of hydraulic oil discharged from the mechanical oil pump based on a hydraulic pressure of the second oil passage generated by the electric oil pump. The hydraulic circuit device described in 1. The supply oil passage has a first supply oil passage for supplying hydraulic oil to the gear mechanism, and a second supply oil passage for supplying hydraulic oil to the motor generator via an oil cooler,
The second spool valve introduces hydraulic oil discharged from the mechanical oil pump into the first supply oil path and the second supply oil path when the hydraulic pressure in the second oil path is lower than a predetermined value. When the hydraulic pressure of the second oil passage is higher than the predetermined value, the hydraulic oil discharged from the electric oil pump is introduced into the first supply oil passage and the machine is switched to the first state possible. The hydraulic circuit device according to claim 2, wherein the hydraulic circuit device is switched to a second state in which hydraulic oil discharged from a hydraulic oil pump is introduced into the second supply oil passage. The mechanical oil pump is configured to rotate in conjunction with an output shaft that transmits a driving force of a vehicle engine to wheels,
The control part which controls the discharge amount of the said electrically driven oil pump based on the vehicle speed, the engine speed, and the temperature of the said motor generator is provided, The any one of Claims 1-3 characterized by the above-mentioned. The hydraulic circuit device described.

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