Motor-integrated driving device

Abstract

To provide a motor-integrated driving device capable of efficiently cooling a motor and expanding a range of a motor rotation speed and an output torque.SOLUTION: An inverter (4) includes a heat exchange portion (41) through which a first refrigerant (40) cooled outside flows, a motor (200) includes a heat exchange passage (21) that cools a second refrigerant (10) from a motor-side storage portion (20) storing the second refrigerant (10) via the heat exchange portion (41), and a gear-side passage (31) that supplies the second refrigerant (10) in a gear-side storage portion (30) to a gear unit (301). The heat exchange passage (21) is connected to one or both of a coil-side passage (23) supplying the second refrigerant (10) to a coil (211) side and a magnet-side passage (22) supplying the second refrigerant (10) to a magnet (221) side, and a flow passage cross-sectional area (S1) of the heat exchange passage (21) is larger than a flow passage cross-sectional area (S2) of the coil-side passage (23) and a flow passage cross-sectional area (S3) of the magnet-side passage (22).SELECTED DRAWING: Figure 1

Description

[Technical Field]

[0001] The present disclosure relates to an electromechanical integrated drive device. [Background technology]

[0002] In conventional electromechanical integrated drive units, a technology is known that eliminates the need for an oil cooler separate from the drive unit by using a cooler mounted on the inverter to exchange heat between the oil circulating inside the motor and the cooling water flowing through the inverter (see, for example, Patent Document 1). [Prior art documents] [Patent documents]

[0003] [Patent Document 1] Japanese Patent Publication No. 2020-54185 Summary of the Invention [Problem to be solved by the invention]

[0004] In conventional electromechanical integrated drive units, the oil reservoir in the motor or the oil circulation path is cooled via the housing by an inverter cooler. The cooled oil is used in a circulation path that is used for both lubricating and cooling the gears and cooling the motor. In this cooling path configuration, oil cooled to the same temperature is used to cool the gears, which generate less heat, and the motor, which generates more heat. In this case, compared to when focusing on cooling only the oil used to cool the motor, the range of motor speed and output torque is narrowed in order to meet the motor's heat resistance temperature.

[0005] The present disclosure discloses technology for solving the above-mentioned problems, and aims to provide an electromechanical integrated drive device that can efficiently cool the motor and expand the range of motor rotation speed and output torque. [Means for solving the problem]

[0006] The electromechanical integrated drive device of the present disclosure comprises: a motor housing portion for housing a motor; an inverter that supplies power to drive the motor; a gear housing section that houses a gear unit that transmits the output torque of the motor; the inverter is cooled by a heat exchanger through which an externally cooled first refrigerant flows; The motor housing section is a motor-side reservoir for storing a second refrigerant; a heat exchange passage that branches off from the motor-side reservoir and cools the second refrigerant through the heat exchange portion, The gear storage section is a gear-side reservoir that stores the second refrigerant that overflows from the motor-side reservoir; a gear-side passage that supplies the second refrigerant in the gear-side reservoir to the gear unit, The heat exchange passage is the passage is connected to either one or both of a coil-side passage that supplies the second refrigerant to the coil side of the motor and a magnet-side passage that supplies the second refrigerant to the magnet side of the motor; The cross-sectional area of ​​the heat exchange passage is larger than the cross-sectional area of ​​the coil-side passage and the cross-sectional area of ​​the magnet-side passage. [Effects of the Invention]

[0007] According to the electromechanical integrated drive device of the present disclosure, The motor can be cooled efficiently, and the range of motor rotation speed and output torque can be expanded. [Brief explanation of the drawings]

[0008] [Figure 1] 1 is a cross-sectional view showing the configuration of a mechanically and electrically integrated drive device according to a first embodiment. [Figure 2] 2 is a cross-sectional view showing the cross section of the electromechanical integrated driving device shown in FIG. 1 taken along line AA. [Figure 3]2 is a cross-sectional view showing a cross section of the electromechanical integrated drive device shown in FIG. 1 along line BB. [Figure 4] 2 is a partially enlarged cross-sectional view of the electromechanical integrated drive device shown in FIG. 1. [Figure 5] 2 is a block diagram showing the relationship between the cooling order of the first refrigerant and the second refrigerant and the objects to be cooled in the mechanically and electrically integrated drive device shown in FIG. 1. FIG. [Figure 6] 2 is a diagram showing the relationship between the control of each pump and each valve of the electromechanical integrated drive device shown in FIG. 1. FIG. [Figure 7] 2 is a diagram showing the relationship between the operating range of the electromechanical integrated drive device shown in FIG. 1 and the test points of a heat run test. FIG. [Figure 8] FIG. 10 is a cross-sectional view showing the configuration of a mechanically and electrically integrated drive device according to a second embodiment. [Figure 9] 9 is a block diagram showing the relationship between the cooling order of the first and second refrigerants and the objects to be cooled in the mechanically and electrically integrated drive device shown in FIG. 8. FIG. [Figure 10] FIG. 10 is a cross-sectional view showing the configuration of a mechanically and electrically integrated drive device according to a third embodiment. [Figure 11] 11 is a block diagram showing the relationship between the cooling order of the first and second refrigerants and the objects to be cooled in the mechanically and electrically integrated drive device shown in FIG. 10. FIG. [Figure 12] FIG. 10 is a cross-sectional view showing the configuration of a mechanically and electrically integrated drive device according to a fourth embodiment. [Figure 13] 13 is a block diagram showing the relationship between the cooling order of the first and second refrigerants and the objects to be cooled in the mechanically and electrically integrated drive device shown in FIG. 12. FIG. [Figure 14] 13 is a diagram showing the relationship between the control of each pump and each valve of the electromechanical integrated drive device shown in FIG. 12. FIG. [Figure 15] FIG. 2 is a block diagram showing the hardware configuration of each control unit in each embodiment. DETAILED DESCRIPTION OF THE INVENTION

[0009] Embodiment 1 Fig. 1 is a cross-sectional view showing the configuration of a mechanically and electrically integrated driving device according to embodiment 1. Fig. 2 is a cross-sectional view showing a cross section of the mechanically and electrically integrated driving device shown in Fig. 1 taken along line AA. Fig. 3 is a cross-sectional view showing a cross section of the mechanically and electrically integrated driving device shown in Fig. 1 taken along line BB. Fig. 4 is a partially enlarged cross-sectional view of the mechanically and electrically integrated driving device shown in Fig. 1. Fig. 5 is a block diagram showing the relationship between the cooling order of the first refrigerant and the second refrigerant and the objects to be cooled in the mechanically and electrically integrated driving device shown in Fig. 1.

[0010] Fig. 6 is a diagram showing the control relationship between each pump and each valve of the electromechanical integrated drive device shown in Fig. 1. Fig. 7 is a diagram showing the relationship between the operating range of the electromechanical integrated drive device shown in Fig. 1 and the test points of the heat run test. In each diagram, dotted arrows indicate the flow of a first refrigerant 40, which will be described later, and solid arrows indicate the flow of a second refrigerant 10, which will be described later. This also applies to other embodiments, so explanations thereof will be omitted as appropriate.

[0011] 1 and 3, the electromechanical integrated drive device 1 has a motor housing section 2, a gear housing section 3, and an inverter 4 integrally formed within a casing 100. A motor 200 is housed in the motor housing section 2. The motor 200 includes a stator 201, a rotor 202, and a shaft 203. The stator 201 is fixed to the casing 100 by a fixing section 212, and is formed by winding a plurality of coils 211 around a stator core 223.

[0012] The rotor 202 is installed radially inside the stator 201 via a predetermined gap, and a plurality of magnets 221 are installed in the rotor core 222. The shaft 203 passes through the center of the rotor 202, holding it and rotating it. The gear housing 3 houses a gear unit 301 that transmits the output torque of the motor 200. Therefore, the shaft 203 of the motor 200 is formed to extend to the gear housing 3 side in order to transmit the output torque of the motor 200 to the gear unit 301. The coil 211 and the magnet 221 are the high-temperature parts of the motor 200. The heat of the coil 211 is transferred to the stator core 223, and the heat of the magnet 221 is transferred to the rotor core 222.

[0013] The inverter 4 is installed below the motor housing section 2 and supplies power to drive the motor 200. The inverter 4 is cooled by a heat exchange section 41 through which a first refrigerant 40 (see FIG. 4), such as water, flows that is cooled by a radiator 91 and an electric pump 92 (see FIG. 5) external to the electro-mechanical integrated drive device 1. As shown in FIGS. 1 and 5, the motor housing section 2 includes a motor-side reservoir 20, a heat exchange passage 21, a coil-side passage 23, a magnet-side passage 22, a pump 25, a pump control section 251, a valve 26 as a branch section, a valve control section 261 as a branch control section, a discharge section 27, and a communication passage 24.

[0014] Motor-side reservoir 20 is formed below the installation position of motor 200 in motor housing 2, and stores a second refrigerant 10 (see FIG. 4), for example, oil. Heat exchange passage 21 branches off from motor-side reservoir 20, and second refrigerant 10 circulating from motor-side reservoir 20 is cooled via heat exchange section 41. Therefore, in order to improve the cooling efficiency of second refrigerant 10, heat exchange passage 21 is formed along heat exchange section 41. Coil-side passage 23 supplies second refrigerant 10 to the coil 211 side of motor 200.

[0015] Second refrigerant 10 supplied to motor 200 from coil-side passage 23 eventually falls within motor housing 2 and returns to motor-side reservoir 20. Magnet-side passage 22 supplies second refrigerant 10 to the magnet 221 side of motor 200, passes through a hollow flow path within shaft 203, and directly cools rotor core 222 of rotor 202 by centrifugal force. Second refrigerant 10 supplied to motor 200 from magnet-side passage 22 eventually falls within motor housing 2 and returns to motor-side reservoir 20.

[0016] The supply of second refrigerant 10 from coil side passage 23 to coil 211 side and from magnet side passage 22 to magnet 221 side are performed by dripping or spraying. The positions of the holes used to supply second refrigerant 10 from coil side passage 23 to coil 211 side (the positions where second refrigerant 10 is discharged in FIG. 1 ) and the positions of the holes used to supply second refrigerant 10 from magnet side passage 22 to magnet 221 side (the positions where second refrigerant 10 is discharged in FIG. 1 ) shown in FIG. 1 are merely examples, and any positions that can cool the coil 211 side and the magnet 221 side are acceptable, and the number of holes is not limited to that shown in FIG. 1 . This also applies to the following embodiments, so further description will be omitted.

[0017] In the first embodiment, heat exchange passage 21 is connected to both coil side passage 23 and magnet side passage 22. Pump 25 is installed on the outlet side of heat exchange passage 21, i.e., the side opposite to the side connected to motor side reservoir 20, and circulates second refrigerant 10 from heat exchange passage 21 to coil side passage 23 and magnet side passage 22 via communication passage 24. Pump control section 251 controls the discharge flow rate of second refrigerant 10 from pump 25.

[0018] Valve 26 is connected to communication passage 24, and branches into coil side passage 23 and magnet side passage 22. Valve control unit 261 controls the flow division ratio of valve 26. When second refrigerant 10 stored in motor side reservoir 20 overflows, discharge unit 27 discharges it into gear side reservoir 30, which will be described later. Valve control unit 261 and pump control unit 251 control valve 26 to change the flow division ratio of second refrigerant 10 flowing into coil side passage 23 and magnet side passage 22, in accordance with the coil temperature of coil 211 of stator 201 of motor 200 and the magnet temperature of magnet 221 of rotor 202, and further control the discharge flow rate of pump 25.

[0019] Here, the flow path cross-sectional area of ​​each passage will be described. The flow path cross-sectional area here refers to the cross-sectional area of ​​the passage perpendicular to the flow direction of second refrigerant 10 flowing through the passage. Therefore, the cross-sectional area of ​​each passage shown in FIG. 3 is the flow path cross-sectional area of ​​each passage. As shown in FIG. 3, the flow path cross-sectional area S1 of heat exchange passage 21 is larger than the flow path cross-sectional area S2 of coil-side passage 23 and the flow path cross-sectional area S3 of magnet-side passage 22. The relationship between the flow path cross-sectional area S1 of heat exchange passage 21, the flow path cross-sectional area S2 of coil-side passage 23, and the flow path cross-sectional area S3 of magnet-side passage 22 is the same in the following embodiments, so description thereof will be omitted as appropriate.

[0020] 4, heat exchanger 41 of inverter 4 is formed with fins 411 protruding toward heat exchange passage 21 and fins 412 protruding toward the side where first refrigerant 40 flows, thereby improving heat exchange efficiency. This also applies to the following embodiments, and therefore a description thereof will be omitted as appropriate.

[0021] The gear storage section 3 includes a gear-side reservoir 30, a gear-side passage 31, a gear-side pump 32, a gear-side pump control section 321, and a return section 33. The gear-side reservoir 30 stores the second refrigerant 10 that overflows from the motor-side reservoir 20. The gear-side passage 31 supplies the second refrigerant 10 to the gear unit 301. The gear-side pump 32 circulates the second refrigerant 10 in the gear-side reservoir 30 to the gear-side passage 31.

[0022] The gear-side pump 32 may be configured as a mechanical oil pump by converting the driving force of the gear unit 301 into the discharge capacity of the gear-side pump 32. By using a mechanical oil pump in this way, cooling performance improves as the operating conditions become higher rotation speeds, which increases mechanical loss in the gear unit 301. In addition, the power consumption of the gear-side pump 32 can be reduced. This also applies to the following embodiments, so a description thereof will be omitted as appropriate.

[0023] Gear-side pump control section 321 controls the discharge flow rate of second refrigerant 10 from gear-side pump 32. Return section 33 returns second refrigerant 10 supplied from gear-side passage 31 to gear unit 301 to motor-side reservoir section 20.

[0024] Next, the flow order of the first refrigerant 40 and the second refrigerant 10 through each passage in the mechanically and electrically integrated drive device 1 of the first embodiment configured as described above will be described with reference to FIG. 5. In FIG. 5, dotted arrows indicate the flow of the first refrigerant 40, and solid arrows indicate the flow of the second refrigerant 10. First, the first refrigerant 40 will be described. The first refrigerant 40 flows through the heat exchanger 41 of the inverter 4 of the mechanically and electrically integrated drive device 1, is discharged from the heat exchanger 41 by an electric pump 92 located outside the mechanically and electrically integrated drive device 1, and is circulated to the radiator 91 where it is cooled. The first refrigerant 40 is then returned to the heat exchanger 41, where it cools the inverter 4 and simultaneously cools the second refrigerant 10 flowing through the heat exchange passage 21. The flow of the first refrigerant 40 is the same in the following embodiments, and therefore description thereof will be omitted where appropriate.

[0025] Next, second refrigerant 10 is stored in motor-side reservoir 20 and flows through heat exchange passage 21, which is connected to motor-side reservoir 20. As described above, when second refrigerant 10 flows through heat exchange passage 21, it is cooled by first refrigerant 40 flowing through heat exchange section 41. This second refrigerant 10 is then supplied to coil-side passage 23 and magnet-side passage 22 via pump 25 controlled by pump control section 251, communication passage 24, and valve 26 controlled by valve control section 261. Second refrigerant 10 supplied to coil-side passage 23 is discharged to the coil 211 side and cools coil 211 (stator core 223), and second refrigerant 10 supplied to magnet-side passage 22 is discharged to the magnet 221 side and cools magnet 221 (rotor core 222), before falling back into motor-side reservoir 20.

[0026] Then, when the amount of second refrigerant 10 stored in motor-side reservoir 8 reaches a specified value, second refrigerant 10 on the gear housing section 3 side overflows from discharge section 27 and is stored in gear-side reservoir 30. Second refrigerant 10 stored in gear-side reservoir 30 is supplied to gear-side passage 31 via gear-side pump 32 controlled by gear-side pump control section 321. Second refrigerant 10 supplied to gear-side passage 31 is then discharged to gear unit 301, cooling gear unit 301. Second refrigerant 10 discharged to gear unit 301 flows along the wall surface of gear housing section 3 (gear unit 301), reaches return section 33, and is collected and returned to motor-side reservoir 20. However, a portion of second refrigerant 10 that does not return to return section 33 falls within gear storage section 3 and returns to gear-side reservoir section 30.

[0027] Next, control of the flow rate of second refrigerant 10 supplied to each passage in mechanically and electrically integrated drive device 1 of embodiment 1 configured as described above will be described with reference to Fig. 6. In Fig. 6, the flow rate in coil side passage 23 is indicated as the "coil side flow rate," and the flow rate in magnet side passage 22 is indicated as the "magnet side flow rate." The flow division ratio of valve 26 is also indicated as the "flow division ratio."

[0028] Here, the following description will be given using the coil threshold temperature Tc of the coil 211 of the motor 200, the magnet threshold temperature Tm of the magnet 221 of the motor 200, the coil temperature T1 of the coil 211 of the motor 200, and the magnet temperature T2 of the magnet 221 of the motor 200. Note that if this point is similar to the following embodiments, the description will be omitted as appropriate.

[0029] First, in Figure 6, when T1 ≤ Tc and T2 ≤ Tm, Pump control unit 251 controls pump 25 to set the discharge flow rate of second refrigerant 10 from pump 25 to a minimum discharge flow rate Q0 determined by pump 25. Then, valve control unit 261 controls valve 26 to allow the entire amount of second refrigerant 10 to flow to coil side passage 23. In other words, valve 26 is controlled so that second refrigerant 10 does not flow to magnet side passage 22.

[0030] In addition, in FIG. 6, when T1≧Tc and T2≦Tm, Pump control section 251 controls pump 25 to increase the discharge flow rate of second refrigerant 10 as coil temperature T1 increases.

[0031] Specifically, the flow rate Qc of the second refrigerant 10 in the coil side passage 23 is Qc=a×(T1-Tc)+Q0 The slope a is determined by the following formula: Slope a=(maximum flow rate of the coil side passage 23−minimum flow rate of the coil side passage 23) / (coil upper limit temperature−coil threshold temperature Tc) Valve control unit 261 then controls valve 26 to allow the entire amount of second refrigerant 10 to flow to coil side passage 23. In other words, valve 26 is controlled so that second refrigerant 10 does not flow to magnet side passage 22.

[0032] Also, in FIG. 6, when T1≦Tc and T2≧Tm, As the magnet temperature T2 increases, the pump control unit 251 and the valve control unit 261 control the pump 25 and the valve 26 so as to maintain the flow rate Qc of the second refrigerant 10 in the coil side passage 23 at a constant amount, in this case the minimum discharge flow rate Q0 determined by the pump 25, and to increase the flow rate Qm of the second refrigerant 10 in the magnet side passage 22.

[0033] Specifically, the flow rate Qm of the second refrigerant 10 in the magnet side passage 22 is Qm = b × (T2 - Tm) The slope b is determined by the following formula: Slope b = (maximum flow rate of magnet side passage 22 - minimum flow rate of magnet side passage 22) / (magnet upper limit temperature - magnet threshold temperature Tm)

[0034] In order to realize the above flow rate, the pump control unit 251 controls the discharge flow rate of the pump 25 to be Q0+Qm. The valve 15 is configured such that the branch flow ratio Rc is set to the coil side passage 23 side as a reference, as follows: Rc=Q0 / (Q0+Qm) The control is performed so as to satisfy the following.

[0035] In addition, in FIG. 6, when T1≧Tc and T2≧Tm, The pump control unit 251 and the valve control unit 261 control the pump 25 and the valve 26 so that the flow rate Qc of the second refrigerant 10 in the coil side passage 23 increases as the coil temperature T1 increases, and the flow rate Qm of the second refrigerant 10 in the magnet side passage 22 increases as the magnet temperature T2 increases.

[0036] Specifically, the flow rate Qc of the second refrigerant 10 in the coil side passage 23 is Qc=a×(T1-Tc)+Q0 The gradient a is the same as that shown above. Furthermore, the flow rate Qm of the second refrigerant 10 in the magnet side passage 22 is Qm = b × (T2 - Tm) The gradient b is the same as that shown above.

[0037] To achieve these flow rates, the pump control unit 251 controls the discharge flow rate of the pump 25 to be Qc+Qm. The valve 15 is configured such that the branch flow ratio Rc is set to the coil side passage 711 side as follows: Rc=Qc / (Qc+Qm) The control is performed so as to satisfy the following.

[0038] The coil threshold temperature Tc is determined by subtracting the maximum value of the temperature of the coil 211 that changes during the time required to change the flow rate and the temperature margin from the heat resistance temperature of the insulating material of a portion of the coil 211, so as not to exceed the coil's heat resistance temperature. The coil's heat resistance temperature is set depending on the type of coil, and is 180°C when polyesterimide wire is used, for example. In this embodiment, if the temperature margin, which takes into account the sensor error and variation of the sensor that measures the temperature of the coil 211, is set to, for example, 10°C, the upper coil temperature limit is 170°C.

[0039] Here, we will explain how to calculate the maximum temperature of coil 211 that changes during the time it takes to change the flow rate. As shown in Figure 7, heat run test 1 (the point where heat run test 1 is performed in Figure 7: the operating point where the coil temperature is maximum) is performed at the minimum discharge flow rate Q0 determined by pump 25 at the operating point where motor rotation speed n is maximum within the motor operating range where the current flowing through coil 211 is maximum, and coil temperature T1 is calculated from the results of actual measurements. From the temperature waveform of the actual measurement results, the increase in coil temperature T1 over the time until the cooling performance of second refrigerant 10 changes is read. Magnet threshold temperature Tm of magnet 221 is determined by subtracting the temperature margin and the maximum value of the temperature of magnet 221 that changes during the time it takes to change the flow rate from the magnet heat resistance temperature of magnet 221 so as not to exceed the magnet heat resistance temperature.

[0040] The magnet heat resistance temperature is set depending on the type of magnet 221 so as not to cause irreversible demagnetization, for example, it is 150°C when a highly heat-resistant neodymium magnet is used. In this embodiment, if the temperature margin that takes into account the sensor error and variation of the sensor that measures the temperature of magnet 221 is set to 10°C, the upper magnet temperature limit will be 140°C.

[0041] Next, we will explain how to calculate the maximum temperature of magnet 221 that changes during the time it takes to change the flow rate. As shown in Figure 7, at the operating point where coil current i is at its maximum within the operating range where motor rotation speed n is at its maximum, heat run test 2 is performed by operating at the minimum discharge flow rate Q0 determined by pump 25 (heat run test 2 execution point in Figure 7: maximum magnet temperature operating point), and the magnet temperature T2 is calculated from the results of the actual measurement.

[0042] From the temperature waveform of the actual measurement results, the rise in magnet temperature T2 during the time until the cooling performance of second refrigerant 10 changes is read. Note that the time until the cooling performance of second refrigerant 10 changes after the command to change the flow rate is calculated as the sum of the communication time of each control unit, the time it takes for pump 25 to change the flow rate, and the time it takes for second refrigerant 10 to arrive after the flow rate change. Note that the method of calculating each value using the concept shown in Figure 7 can be similarly used in the following embodiments, so explanations thereof will be omitted where appropriate.

[0043] It is assumed that the coil temperature T1 and magnet temperature T2 used in each control unit are read from a temperature sensor mounted on the motor 200, or that the coil temperature T1 and magnet temperature T2 are estimated from a map based on actual measurement results or calculations by thermal analysis using the motor input current read from a current sensor and the motor rotation speed read from a rotation angle sensor. This also applies to the following embodiments, so explanations thereof will be omitted where appropriate.

[0044] According to the electromechanical integrated drive device of the first embodiment configured as described above, a motor housing portion for housing a motor; an inverter that supplies power to drive the motor; a gear housing section that houses a gear unit that transmits the output torque of the motor; the inverter is cooled by a heat exchanger through which an externally cooled first refrigerant flows; The motor housing section is a motor-side reservoir for storing a second refrigerant; a heat exchange passage that branches off from the motor-side reservoir and cools the second refrigerant through the heat exchange portion, The gear storage section is a gear-side reservoir that stores the second refrigerant that overflows from the motor-side reservoir; a gear-side passage that supplies the second refrigerant in the gear-side reservoir to the gear unit, The heat exchange passage is the passage is connected to either one or both of a coil-side passage that supplies the second refrigerant to the coil side of the motor and a magnet-side passage that supplies the second refrigerant to the magnet side of the motor; The cross-sectional area of ​​the heat exchange passage is larger than the cross-sectional area of ​​the coil side passage and the cross-sectional area of ​​the magnet side passage. So, The motor can be cooled efficiently, and the range of motor rotation speed and output torque can be expanded. Furthermore, there is no need to place a cooler for the second refrigerant outside the electromechanical integrated drive device, which saves space compared to when a cooler is placed outside.

[0045] Furthermore, according to the electromechanical integrated drive device of the first embodiment configured as described above, the gear storage section has a return section that returns the second refrigerant supplied from the gear-side passage to the gear unit to the motor-side reservoir section, the heat exchange passage is connected to both the coil side passage and the magnet side passage, a branching portion that branches off the coil side passage and the magnet side passage; a branch control unit for controlling a branch ratio of the branch unit; a pump that is installed on the outlet side of the heat exchange passage and circulates the second refrigerant to the coil side passage and the magnet side passage; a pump control unit that controls a discharge flow rate of the second refrigerant from the pump, The branch control unit and the pump control unit control a flow division ratio of the second refrigerant flowing into the coil side passage and the magnet side passage and a discharge flow rate of the pump according to a coil temperature and a magnet temperature of the motor. So, By separating the circulation through the coil side passage and magnet side passage from the circulation through the gear motor side passage, it is possible to focus on cooling the second refrigerant used to cool the coil and magnet, which are high-temperature parts of the motor, and the temperature of the second refrigerant in the coil side passage and magnet side passage can be kept lower than the temperature of the second refrigerant in the gear motor side passage. In addition, by reducing the temperature of the second refrigerant used to cool the motor, it is possible to reduce the size of a motor with the same output and improve motor output. In addition, by increasing the temperature of the second refrigerant in the gear motor side passage, mechanical loss due to friction in the gear unit can be reduced, improving the efficiency of the electromechanical integrated drive device.

[0046] Furthermore, according to the electromechanical integrated drive device of the first embodiment configured as described above, Assuming that the coil threshold temperature of the motor is Tc, the magnet threshold temperature of the motor is Tm, the coil temperature of the motor is T1, and the magnet temperature of the motor is T2, When T1 ≤ Tc, T2 ≤ Tm, the pump control unit controls the pump so that the discharge flow rate of the second refrigerant from the pump is a minimum discharge flow rate determined by the pump; The branch control unit controls the branch unit so that the entire amount of the second refrigerant flows into the coil side passage. So, By controlling the pump and valve so that the flow rate of the second refrigerant and the valve's flow division ratio are appropriate according to the motor's coil and magnet temperatures, it is possible to prevent overcooling, reduce the pump's power consumption, and improve the cooling performance for the coil and magnet, thereby increasing the motor's maximum torque and maximum rotation speed.

[0047] Furthermore, according to the electromechanical integrated drive device of the first embodiment configured as described above, Assuming that the coil threshold temperature of the motor is Tc, the magnet threshold temperature of the motor is Tm, the coil temperature of the motor is T1, and the magnet temperature of the motor is T2, When T1 ≥ Tc, T2 ≤ Tm, the pump control unit controls the pump to increase the discharge flow rate of the second refrigerant as the coil temperature T1 increases, The branch control unit controls the branch unit so that the entire amount of the second refrigerant flows into the coil side passage. So, By controlling the pump and valve so that the flow rate of the second refrigerant and the valve's flow division ratio are appropriate according to the motor's coil and magnet temperatures, it is possible to prevent overcooling, reduce the pump's power consumption, and improve the cooling performance for the coil and magnet, thereby increasing the motor's maximum torque and maximum rotation speed.

[0048] Furthermore, according to the electromechanical integrated drive device of the first embodiment configured as described above, Assuming that the coil threshold temperature of the motor is Tc, the magnet threshold temperature of the motor is Tm, the coil temperature of the motor is T1, and the magnet temperature of the motor is T2, When T1≦Tc, T2≧Tm, As the magnet temperature T2 increases, the flow rate of the second refrigerant in the coil side passage is kept constant and the flow rate of the second refrigerant in the magnet side passage is increased. The pump control unit and the branch control unit control the pump and the branch unit. So, By controlling the pump and valve so that the flow rate of the second refrigerant and the valve's flow division ratio are appropriate according to the motor's coil and magnet temperatures, it is possible to prevent overcooling, reduce the pump's power consumption, and improve the cooling performance for the coil and magnet, thereby increasing the motor's maximum torque and maximum rotation speed.

[0049] Furthermore, according to the electromechanical integrated drive device of the first embodiment configured as described above, Assuming that the coil threshold temperature of the motor is Tc, the magnet threshold temperature of the motor is Tm, the coil temperature of the motor is T1, and the magnet temperature of the motor is T2, When T1 ≥ Tc and T2 ≥ Tm, the flow rate of the second refrigerant in the coil side passage is increased as the coil temperature T1 increases, and the flow rate of the second refrigerant in the magnet side passage is increased as the magnet temperature T2 increases, The pump control unit and the branch control unit control the pump and the branch unit. So, By controlling the pump and valve so that the flow rate of the second refrigerant and the valve's flow division ratio are appropriate according to the motor's coil and magnet temperatures, it is possible to prevent overcooling, reduce the pump's power consumption, and improve the cooling performance for the coil and magnet, thereby increasing the motor's maximum torque and maximum rotation speed.

[0050] Furthermore, according to the electromechanical integrated drive device of the first embodiment configured as described above, The coil temperature T1 and the magnet temperature T2 are Use a value estimated using the motor input current of the motor, or Use the value estimated using the motor rotation speed of the motor So, It can detect and control various temperatures.

[0051] Furthermore, according to the electromechanical integrated drive device of the first embodiment configured as described above, A fin portion is formed between the heat exchange passage and the heat exchange portion, on either or both of the first refrigerant side and the second refrigerant side. So, The fin portion makes it possible to increase the heat transfer area, thereby efficiently reducing the temperature of the second refrigerant.

[0052] Furthermore, according to the electromechanical integrated drive device of the first embodiment configured as described above, the heat exchanger is disposed below the motor-side reservoir; The heat exchange passage is formed below the motor-side reservoir along the heat exchange portion. So, The thermal resistance between the heat exchange section of the inverter and the heat exchange passage can be reduced, and the heat of the second refrigerant used to cool the motor can be efficiently dissipated via the heat exchange section of the inverter.

[0053] Furthermore, according to the electromechanical integrated drive device of the first embodiment configured as described above, The second refrigerant is circulated from the gear-side reservoir to the gear-side passage by the driving force of the gear unit. So, The cooling performance improves as the operating conditions become higher, which increases the mechanical loss of the gear unit. Also, the power consumption of the gear pump can be reduced.

[0054] Embodiment 2 Fig. 8 is a cross-sectional view showing the configuration of a mechanically and electrically integrated drive device according to embodiment 2. Fig. 9 is a block diagram showing the relationship between the cooling order of the first and second refrigerants and the objects to be cooled in the mechanically and electrically integrated drive device shown in Fig. 8. In the figure, parts that are the same as those in embodiment 1 above are given the same reference numerals and descriptions thereof will be omitted.

[0055] In the first embodiment described above, an example was shown in which heat exchange passage 21 was connected to both the coil side passage 23 and the magnet side passage 22. However, in the second embodiment, an example will be described in which heat exchange passage 21 is connected only to the coil side passage 23, as shown in FIG. 8 . Gear side passage 31 is connected to magnet side passage 22. Pump 25 is installed on the outlet side of heat exchange passage 21 and corresponds to a first pump that circulates second refrigerant 10 to coil side passage 23. Pump control unit 251 corresponds to a first pump control unit that controls the discharge flow rate of second refrigerant 10 from pump 25, which serves as the first pump.

[0056] Gear-side pump 32 corresponds to a second pump that is installed in gear-side reservoir 30 and circulates second refrigerant 10 to magnet-side passage 22 via gear-side passage 31. Gear-side pump control unit 321 corresponds to a second pump control unit that controls the discharge flow rate of second refrigerant 10 from gear-side pump 32 serving as the second pump. Pump control unit 251 and gear-side pump control unit 321 control the discharge flow rates of pump 25 and gear-side pump 32 in accordance with coil temperature T1 and magnet temperature T2 of motor 200.

[0057] Next, the flow order of the first refrigerant 40 and the second refrigerant 10 through each passage in the mechanically and electrically integrated drive device 1 of the second embodiment configured as described above will be described with reference to Figure 9. In Figure 9, dotted arrows indicate the flow of the first refrigerant 40, and solid arrows indicate the flow of the second refrigerant 10. First, the first refrigerant 40 is the same as in the first embodiment.

[0058] Next, second refrigerant 10 is stored in motor-side reservoir 20, and as in the first embodiment, is cooled in heat exchange passage 21 that is connected thereto by first refrigerant 40 circulating in heat exchange section 41. Then, this second refrigerant 10 is supplied to coil-side passage 23 via pump 25 controlled by pump control section 251. Then, second refrigerant 10 supplied to coil-side passage 23 is discharged to the coil 211 side, cools coil 211 (stator core 223), and drops back down into motor-side reservoir 20.

[0059] Then, as in the first embodiment, second refrigerant 10 stored in motor-side reservoir 8 on the gear housing unit 3 side is supplied to gear-side passage 31 and magnet-side passage 22 via gear-side pump 32 controlled by gear-side pump control unit 321. Second refrigerant 10 supplied to gear-side passage 31 is then discharged into gear unit 301, cooling gear unit 301. Second refrigerant 10 discharged into gear unit 301 falls within gear housing unit 3 and returns to gear-side reservoir 30. Second refrigerant 10 supplied to magnet-side passage 22 is discharged toward magnet 221, cools magnet 221 (rotor core 222), and falls back into motor-side reservoir 20.

[0060] Next, the control of the flow of the second refrigerant 10 through each passage of the mechatronic drive device 1 of Embodiment 2 configured as described above will be explained. First, the pump control unit 251 of the pump 25 When T1 < Tc, sets the discharge flow rate of the second refrigerant 10 of the pump 25 to the minimum discharge flow rate Q0 determined by the pump 25.

[0061] Also, the pump control unit 251 of the pump 25 When T1 ≥ Tc, controls the discharge flow rate Qc1 of the second refrigerant 10 of the pump 25 to increase as the coil temperature T1 increases. Specifically, the discharge flow rate Qc1 of the second refrigerant 10 of the pump 25 is Qc1 = a × (T1 - Tc) + Q0 and is determined to satisfy this. The slope a is determined in the same manner as in Embodiment 1 above.

[0062] Next, the gear side pump control unit 321 of the gear side pump 32 When T2 < Tm, sets the discharge flow rate of the second refrigerant of the gear side pump to the minimum discharge flow rate Q0 determined by the gear side pump 32.

[0063] Also, the gear side pump control unit 321 of the gear side pump 32 When T2 ≥ Tm, controls the discharge flow rate of the second refrigerant of the gear side pump to increase as the magnet temperature T2 increases. Specifically, the flow rate Qm of the second refrigerant 10 in the magnet side passage 22 is Qm = b × (T2 - Tm) and is determined to satisfy this. The slope b is determined in the same manner as in Embodiment 1 above.

[0064] According to the mechatronic drive device of Embodiment 2 configured as described above, the same effects as those of Embodiment 1 are achieved, and the heat exchange passage is connected to the coil side passage, The gear-side passage is connected to the magnet-side passage, a first pump installed on the outlet side of the heat exchange passage for circulating the second refrigerant to the coil-side passage, a first pump control unit for controlling the discharge flow rate of the second refrigerant of the first pump, a second pump installed in the gear-side storage section for circulating the second refrigerant to the magnet-side passage through the gear-side passage, and a second pump control unit for controlling the discharge flow rate of the second refrigerant of the second pump. The first pump control unit and the second pump control unit control the discharge flow rates of the first pump and the second pump according to the coil temperature and the magnet temperature of the motor. Therefore, since the second refrigerant cooled by the heat exchange section of the inverter can be directly supplied only to the coil side, the current range that can be passed through the motor can be expanded, and the motor can be made to have a higher output.

[0065] Furthermore, according to the electromechanical integrated drive device of Embodiment 2 configured as described above, the same effects as those of Embodiment 1 are achieved, and assuming that the coil threshold temperature Tc of the motor, the magnet threshold temperature Tm of the motor, the coil temperature T1 of the motor, and the magnet temperature T2 of the motor, the first pump control unit when T1 < Tc, sets the discharge flow rate of the second refrigerant of the first pump as the minimum discharge flow rate determined by the first pump, when T1 ≥ Tc, controls the discharge flow rate of the second refrigerant of the first pump to increase as the coil temperature T1 increases. Therefore, by controlling the first pump so that the flow rate of the second refrigerant becomes appropriate according to the coil temperature and the magnet temperature of the motor, overcooling can be prevented, the power consumption of the pump can be reduced, and the cooling performance for the coil and the magnet can be improved, thereby expanding the maximum torque and the maximum rotational speed of the motor.

[0066] Furthermore, according to the electromechanical integrated drive device of Embodiment 2 configured as described above, the same effects as those of Embodiment 1 are achieved, and assuming that the coil threshold temperature Tc of the motor, the magnet threshold temperature Tm of the motor, the coil temperature T1 of the motor, and the magnet temperature T2 of the motor, the second pump control unit, when T2 < Tm, the discharge flow rate of the second refrigerant of the second pump is set as the minimum discharge flow rate determined by the second pump, when T2 ≥ Tm, the discharge flow rate of the second refrigerant of the second pump is controlled to increase as the magnet temperature T2 increases therefore, by controlling the second pump so that the flow rate of the second refrigerant is appropriate according to the coil temperature and the magnet temperature of the motor, overcooling can be prevented, the power consumption of the pump can be reduced, and the cooling performance for the coil and the magnet can be improved. As a result, the maximum torque and the maximum rotational speed of the motor can be expanded.

[0067] Embodiment 3. FIG. 10 is a cross-sectional view showing the configuration of the electromechanical integrated drive device according to Embodiment 3. FIG. 11 is a block diagram showing the relationship between the cooling order of the first refrigerant and the second refrigerant and the cooling targets of the electromechanical integrated drive device shown in FIG. 10. In the figures, the same parts as those in the above embodiments are denoted by the same reference numerals and the description thereof is omitted.

[0068] In the above Embodiment 1, the heat exchange passage 21 is connected to both the coil-side passage 23 and the magnet-side passage 22. In the above Embodiment 2, an example in which the heat exchange passage 21 is connected only to the coil-side passage 23 is shown. However, in the present Embodiment 3, as shown in FIG. 10, an example in which the heat exchange passage 21 is connected only to the magnet-side passage 22 will be described. And the gear-side passage 31 is connected to the coil-side passage 23.

[0069] Pump 25 is installed on the outlet side of heat exchange passage 21 and corresponds to a first pump that circulates second refrigerant 10 to coil side passage 23. Pump control unit 251 corresponds to a first pump control unit that controls the discharge flow rate of second refrigerant 10 from pump 25 as the first pump. Gear side pump 32 is installed in gear side reservoir 30 and corresponds to a second pump that circulates second refrigerant 10 to coil side passage 23 via gear side passage 31.

[0070] The gear-side pump control unit 321 corresponds to a second pump control unit that controls the discharge flow rate of the second refrigerant 10 from the gear-side pump 32 serving as the second pump. The pump control unit 251 and the gear-side pump control unit 321 control the discharge flow rates of the pump 25 and the gear-side pump 32 in accordance with the coil temperature T1 and the magnet temperature T2 of the motor 200.

[0071] Next, the flow order of the first refrigerant 40 and the second refrigerant 10 through each passage in the mechanically and electrically integrated drive device 1 of the third embodiment configured as described above will be described with reference to Fig. 11. In Fig. 11, dotted arrows indicate the flow of the first refrigerant 40, and solid arrows indicate the flow of the second refrigerant 10. First, the first refrigerant 40 is the same as in each of the above embodiments.

[0072] Next, second refrigerant 10 is stored in motor-side reservoir 20, and as in each of the above embodiments, is cooled in heat exchange passage 21 that is connected thereto by first refrigerant 40 circulating in heat exchange section 41. Then, this second refrigerant 10 is supplied to magnet-side passage 22 via pump 25 controlled by pump control section 251. Then, second refrigerant 10 supplied to magnet-side passage 22 is discharged to the magnet 221 side, cools magnet 221 (rotor core 222), and drops back down into motor-side reservoir 20.

[0073] And, similar to each of the above embodiments, the second refrigerant 10 stored in the motor-side reservoir 8 on the gear storage part 3 side is supplied to the gear-side passage 31 and the coil-side passage 23 through the gear-side pump 32 controlled by the gear-side pump control part 321. Then, the second refrigerant 10 supplied to the gear-side passage 31 is discharged to the gear unit 301 to cool the gear unit 301. Then, the second refrigerant 10 discharged to the gear unit 301 falls within the gear storage part 3 and returns to the gear-side reservoir 30. Also, the second refrigerant 10 supplied to the coil-side passage 23 is discharged to the coil 211 side to cool the coil 211 (stator core 223) and falls back to the motor-side reservoir 20.

[0074] Next, the control of the flow of the second refrigerant 10 through each passage of the electromechanical integrated drive device 1 of Embodiment 3 configured as described above will be explained. First, the pump control part 251 of the pump 25, when T2 < Tm, sets the discharge flow rate of the second refrigerant 10 of the pump 25 to the minimum discharge flow rate Q0 determined by the pump 25.

[0075] Also, the pump control part 251 of the pump 25, when T2 ≥ Tm, controls the discharge flow rate of the second refrigerant 10 of the pump 25 to increase as the magnet temperature T2 increases. Specifically, the flow rate Qm of the second refrigerant 10 in the magnet-side passage 22 is determined to satisfy Qm = b × (T2 - Tm) where the slope b is determined in the same manner as in each of the above embodiments.

[0076] Next, the gear-side pump control part 321 of the gear-side pump 32, when T1 < Tc, sets the discharge flow rate of the second refrigerant 10 of the gear-side pump 32 to the minimum discharge flow rate Q00 determined by the gear-side pump 32.

[0077] Also, the gear-side pump control part 321 of the gear-side pump 32, when T1 ≥ Tc, Control so that the discharge flow rate of the second refrigerant 10 of the gear-side pump 32 increases as the coil temperature T1 increases. Specifically, the discharge flow rate Qc2 of the second refrigerant 10 of the gear-side pump 32 is Qc2 = a×(T1 - Tc) + Q00 is determined to satisfy. Note that the slope a is determined in the same manner as in each of the above embodiments.

[0078] According to the mechatronic drive device of Embodiment 3 configured as described above, the same effects as those of the above embodiments are achieved, and the heat exchange passage is connected to the magnet-side passage, the gear-side passage is connected to the coil-side passage, a first pump installed on the outlet side of the heat exchange passage to circulate the second refrigerant to the magnet-side passage, a first pump control unit that controls the discharge flow rate of the second refrigerant of the first pump, a second pump installed in the gear-side reservoir to circulate the second refrigerant to the coil-side passage through the gear-side passage, and a second pump control unit that controls the discharge flow rate of the second refrigerant of the second pump. The first pump control unit and the second pump control unit control the discharge flow rates of the first pump and the second pump according to the coil temperature and the magnet temperature of the motor [[ID=2(]] Therefore, since the second refrigerant cooled by the heat exchange unit of the inverter can be directly supplied only to the magnet side, the temperature of the magnet side (magnet and rotor core) can be reduced, and the operating range of the motor rotation speed can be expanded.

[0079] Furthermore, according to the mechatronic drive device of Embodiment 3 configured as described above, the same effects as those of the above embodiments are achieved, and assuming the coil threshold temperature Tc of the motor, the magnet threshold temperature Tm of the motor, the coil temperature T1 of the motor, and the magnet temperature T2 of the motor, the first pump control unit is when T2 < Tm, The discharge flow rate of the second refrigerant of the first pump is set as the minimum discharge flow rate determined by the first pump. When T2 ≥ Tm Control the discharge flow rate of the second refrigerant of the first pump to increase as the magnet temperature T2 increases. Therefore By controlling the first pump according to the coil temperature and the magnet temperature of the motor so that the flow rate of the second refrigerant is appropriate, overcooling can be prevented, the power consumption of the pump can be reduced, while the cooling performance for the coil and the magnet can be improved, thereby expanding the maximum torque and the maximum rotational speed of the motor.

[0080] Furthermore, according to the electromechanical integrated drive device of Embodiment 3 configured as described above, the same effects as those of the above embodiments are achieved, and Assuming the coil threshold temperature Tc of the motor, the magnet threshold temperature Tm of the motor, the coil temperature T1 of the motor, and the magnet temperature T2 of the motor, The second pump control unit When T1 < Tc The discharge flow rate of the second refrigerant of the second pump is set as the minimum discharge flow rate determined by the second pump. When T1 ≥ Tc Control the discharge flow rate of the second refrigerant of the second pump to increase as the coil temperature T1 increases. Therefore By controlling the second pump according to the coil temperature and the magnet temperature of the motor so that the flow rate of the second refrigerant is appropriate, overcooling can be prevented, the power consumption of the pump can be reduced, while the cooling performance for the coil and the magnet can be improved, thereby expanding the maximum torque and the maximum rotational speed of the motor.

[0081] Embodiment 4. Fig. 12 is a cross-sectional view showing the configuration of a mechanically and electrically integrated drive device according to embodiment 4. Fig. 13 is a block diagram showing the relationship between the cooling order of the first refrigerant and the second refrigerant and the objects to be cooled in the mechanically and electrically integrated drive device shown in Fig. 12. Fig. 14 is a diagram showing the control relationship between each pump and each valve of the mechanically and electrically integrated drive device shown in Fig. 12. In the figure, parts that are the same as those in the above embodiments are given the same reference numerals and their explanations will be omitted.

[0082] In the above-mentioned embodiment 1, an example was shown in which the heat exchange passage 21 was connected to both the coil side passage 23 and the magnet side passage 22, in embodiment 2, the heat exchange passage 21 was connected only to the coil side passage 23, and in embodiment 3, the heat exchange passage 21 was connected only to the coil side passage 23. However, in this embodiment 4, as shown in FIG. 10, a case will be described in which the heat exchange passage 21 is connected to both the coil side passage 23 and the magnet side passage 22, and the gear side passage 31 is connected to both the coil side passage 23 and the magnet side passage 22.

[0083] Pump 25 is installed on the outlet side of heat exchange passage 21 and corresponds to a first pump that circulates second refrigerant 10 to coil side passage 23. Pump control unit 251 corresponds to a first pump control unit that controls the discharge flow rate of second refrigerant 10 from pump 25 as the first pump. Gear side pump 32 is installed in gear side reservoir 30 and corresponds to a second pump that circulates second refrigerant 10 to coil side passage 23 via gear side passage 31.

[0084] The gear-side pump control unit 321 corresponds to a second pump control unit that controls the discharge flow rate of the second refrigerant 10 from the gear-side pump 32 serving as the second pump. In the fourth embodiment, the pump control unit 251 controls only the ON / OFF of the pump 25, and the gear-side pump control unit 321 controls only the ON / OFF of the gear-side pump 32.

[0085] Furthermore, in this fourth embodiment, there are provided a first valve 51 as a first opening / closing unit that is installed on the heat exchange passage 21 side of the magnet side passage 22 and opens and closes the flow of second refrigerant 10 to the magnet side passage 22, and a first valve control unit 511 as a first control unit that controls the first valve 51, a second valve 52 as a second opening / closing unit that is installed on the gear side passage 31 side of the magnet side passage 22 and opens and closes the flow of second refrigerant 10 to the magnet side passage 22, and a second valve control unit 521 as a second control unit that controls the second valve 52.

[0086] Furthermore, the system is provided with a third valve 53 as a third opening / closing unit that is installed on the heat exchange passage 21 side of the coil side passage 23 and opens and closes the flow of the second refrigerant 10 to the coil side passage 23, a third valve control unit 531 that also serves as a third control unit that controls the third valve 53, a fourth valve 54 as a fourth opening / closing unit that is installed on the gear side passage 31 side of the coil side passage 23 and opens and closes the flow of the second refrigerant 10 to the coil side passage 23, and a fourth valve control unit 541 that also serves as a fourth control unit that controls the fourth valve 54.

[0087] The first valve control unit 511, the second valve control unit 521, the third valve control unit 531, the fourth valve control unit 541, the pump control unit 251 and the gear-side pump control unit 321 control the opening and closing of the first valve 51, the second valve 52, the third valve 53 and the fourth valve 54 and the ON / OFF of the pump 25 and the gear-side pump 32 according to the coil temperature T1 and the magnet temperature T2 of the motor 200.

[0088] Next, the flow order of the first refrigerant 40 and the second refrigerant 10 through each passage in the mechanically and electrically integrated drive device 1 of the fourth embodiment configured as described above will be described with reference to Fig. 13. In Fig. 13, dotted arrows indicate the flow of the first refrigerant 40, and solid arrows indicate the flow of the second refrigerant 10. First, the first refrigerant 40 is the same as in each of the above embodiments.

[0089] Next, second refrigerant 10 is stored in motor-side reservoir 20 and, as in the above-described embodiments, is cooled in heat exchange passage 21 connected thereto by first refrigerant 40 circulating in heat exchange section 41. This second refrigerant 10 is then supplied to magnet-side passage 22 and coil-side passage 23 via pump 25 controlled by pump control section 251, communication passage 24, first valve 51 controlled by first valve control section 511, or third valve 53 controlled by third valve control section 531. Second refrigerant 10 supplied to magnet-side passage 22 is then discharged toward magnet 221, cooling magnet 221 (rotor core 222), and then dropping back into motor-side reservoir 20. Second refrigerant 10 supplied to coil-side passage 23 is discharged toward coil 211, cooling coil 211 (stator core 223), and then dropping back into motor-side reservoir 20.

[0090] As in each of the above embodiments, the second refrigerant 10 stored in the motor side reservoir 8 on the gear storage section 3 side is supplied to the gear side passage 31, the magnet side passage 22 and the coil side passage 23 via the gear side pump 32 controlled by the gear side pump control section 321, the second valve 52 controlled by the second valve control section 521 or the fourth valve 54 controlled by the fourth valve control section 541.

[0091] The second refrigerant 10 supplied to the gear-side passage 31 is then discharged to the gear unit 301, cooling it. The second refrigerant 10 discharged to the gear unit 301 then drops within the gear storage section 3 and returns to the gear-side reservoir 30. The second refrigerant 10 supplied to the magnet-side passage 22 is discharged to the magnet 221 side, cools the magnet 221 (rotor core 222), and drops back into the motor-side reservoir 20. The second refrigerant 10 supplied to the coil-side passage 23 is discharged to the coil 211 side, cools the coil 211 (stator core 223), and drops back into the motor-side reservoir 20.

[0092] Next, the control of the flow of second refrigerant 10 to each passage in mechanically and electrically integrated driving device 1 of the fourth embodiment configured as above will be described with reference to FIG. First, if T1≦Tc, T2≦Tm, The pump control unit 251 turns off the pump 25, The gear-side pump control unit 321 turns on the gear-side pump 32, The first valve control section 511 closes the first valve 51, The second valve control section 521 opens the second valve 52, The third valve control section 531 closes the third valve 53, The fourth valve control section 541 controls the fourth valve 54 to be open. This allows control so that second refrigerant 10 flows from gear-side passage 31 to coil-side passage 23 and magnet-side passage 22.

[0093] Also, if T1 ≥ Tc and T2 ≤ Tm, The pump control unit 251 turns on the pump 25, The gear-side pump control unit 321 turns on the gear-side pump 32, The first valve control section 511 closes the first valve 51, The second valve control section 521 opens the second valve 52, The third valve control section 531 opens the third valve 53, The fourth valve control unit 541 controls the fourth valve 54 to close it. This allows control so that second refrigerant 10 flows from heat exchange passage 21 to coil side passage 23 and from gear side passage 31 to magnet side passage 22.

[0094] Also, when T1≦Tc and T2≧Tm, The pump control unit 251 turns on the pump 25, The gear-side pump control unit 321 turns on the gear-side pump 32, The first valve control section 511 opens the first valve 51, The second valve control section 521 closes the second valve 52, The third valve control section 531 closes the third valve 53, The fourth valve control section 541 controls the fourth valve 54 to be open. This allows control so that second refrigerant 10 flows from heat exchange passage 21 to magnet side passage 22, and second refrigerant 10 flows from gear side passage 31 to coil side passage .

[0095] Also, when T1 ≥ Tc and T2 ≥ Tm, The pump control unit 251 turns on the pump 25, The gear-side pump control unit 321 turns off the gear-side pump 32, The first valve control section 511 opens the first valve 51, The second valve control section 521 closes the second valve 52, The third valve control section 531 opens the third valve 53, The fourth valve control unit 541 controls the fourth valve 54 to close it. This allows control so that second refrigerant 10 flows from heat exchange passage 21 to coil side passage 23 and magnet side passage 22. In this case, hole H is provided in advance at a location of magnet side passage 22 located inside gear housing section 3 in order to cool gear unit 301.

[0096] Furthermore, the electromechanical integrated drive device of the fourth embodiment configured as described above has the same effects as those of the above embodiments, and also has the following advantages: the heat exchange passage is connected to both the coil side passage and the magnet side passage, the gear-side passage is connected to both the coil-side passage and the magnet-side passage, a first opening / closing unit that is installed on the heat exchange passage side of the magnet side passage and opens and closes the flow of the second refrigerant into the magnet side passage; a first control unit that controls the first opening / closing unit; a second opening / closing unit that is installed on the gear-side passage side of the magnet-side passage and opens and closes the flow of the second refrigerant into the magnet-side passage; a second control unit that controls the second opening / closing unit; a third opening / closing unit that is installed on the heat exchange passage side of the coil side passage and opens and closes the flow of the second refrigerant into the coil side passage; a third control unit that controls the third opening / closing unit; a fourth opening / closing unit that is installed on the gear side passage side of the coil side passage and opens and closes the flow of the second refrigerant to the coil side passage; a fourth control unit that controls the fourth opening / closing unit; a first pump that is installed on an outlet side of the heat exchange passage and that circulates the second refrigerant to the coil side passage and the magnet side passage; a first pump control unit that controls the first pump to turn on and off; a second pump that is installed in the gear-side reservoir and circulates the second refrigerant to the coil-side passage and the magnet-side passage via the gear-side passage; a second pump control unit that controls the second pump to turn on and off, The first control unit, the second control unit, the third control unit, the fourth control unit, the first pump control unit, and the second pump control unit control opening and closing of the first opening and closing unit, the second opening and closing unit, the third opening and closing unit, and the fourth opening and closing unit and turning on and off of the first pump and the second pump according to the coil temperature and the magnet temperature of the motor. So, Depending on the motor coil temperature and magnet temperature, It is possible to select either or both of the following: directly supplying the second refrigerant cooled by the heat exchanger of the inverter only to the coil side, or directly supplying the second refrigerant cooled by the heat exchanger of the inverter only to the magnet side. This makes it possible to achieve both the effects of expanding the range of current that can be passed through the motor, thereby enabling the motor to have higher output, and reducing the temperature on the magnet side (magnet and rotor core), thereby expanding the operating range of the motor rotation speed.

[0097] Furthermore, the electromechanical integrated drive device of the fourth embodiment configured as described above has the same effects as those of the above embodiments, and also has the following advantages: Assuming that the coil threshold temperature of the motor is Tc, the magnet threshold temperature of the motor is Tm, the coil temperature of the motor is T1, and the magnet temperature of the motor is T2, When T1 ≤ Tc, T2 ≤ Tm, the first pump control unit turns off the first pump, the second pump control unit turns on the second pump, The first control unit closes the first opening / closing unit, the second control unit opens the second opening / closing unit, the third control unit closes the third opening / closing unit, The fourth control unit controls the fourth opening / closing unit to be open. So, By appropriately controlling the flow rate of the second refrigerant and the opening and closing of the first, second, third, and fourth open-closed sections in accordance with the coil temperature and magnet temperature of the motor, it is possible to prevent overcooling, reduce the power consumption of the pump, and improve the cooling performance for the coil and magnet, thereby increasing the maximum torque and maximum rotation speed of the motor.

[0098] Furthermore, the electromechanical integrated drive device of the fourth embodiment configured as described above has the same effects as those of the above embodiments, and also has the following advantages: Assuming that the coil threshold temperature of the motor is Tc, the magnet threshold temperature of the motor is Tm, the coil temperature of the motor is T1, and the magnet temperature of the motor is T2, When T1 ≥ Tc, T2 ≤ Tm, the first pump control unit turns on the first pump; the second pump control unit turns on the second pump, The first control unit closes the first opening / closing unit, the second control unit opens the second opening / closing unit, the third control unit opens the third opening / closing unit, The fourth control unit controls the fourth opening / closing unit to close. So, By appropriately controlling the flow rate of the second refrigerant and the opening and closing of the first, second, third, and fourth open-closed sections in accordance with the coil temperature and magnet temperature of the motor, it is possible to prevent overcooling, reduce the power consumption of the pump, and improve the cooling performance for the coil and magnet, thereby increasing the maximum torque and maximum rotation speed of the motor.

[0099] Furthermore, the electromechanical integrated drive device of the fourth embodiment configured as described above has the same effects as those of the above embodiments, and also has the following advantages: Assuming that the coil threshold temperature of the motor is Tc, the magnet threshold temperature of the motor is Tm, the coil temperature of the motor is T1, and the magnet temperature of the motor is T2, When T1≦Tc, T2≧Tm, the first pump control unit turns on the first pump; the second pump control unit turns on the second pump, The first control unit opens the first opening / closing unit, The second control unit closes the second opening / closing unit, the third control unit closes the third opening / closing unit, The fourth control unit controls the fourth opening / closing unit to be open. So, By appropriately controlling the flow rate of the second refrigerant and the opening and closing of the first, second, third, and fourth open-closed sections in accordance with the coil temperature and magnet temperature of the motor, it is possible to prevent overcooling, reduce the power consumption of the pump, and improve the cooling performance for the coil and magnet, thereby increasing the maximum torque and maximum rotation speed of the motor.

[0100] Furthermore, the electromechanical integrated drive device of the fourth embodiment configured as described above has the same effects as those of the above embodiments, and also has the following advantages: Assuming that the coil threshold temperature of the motor is Tc, the magnet threshold temperature of the motor is Tm, the coil temperature of the motor is T1, and the magnet temperature of the motor is T2, When T1 ≥ Tc and T2 ≥ Tm, the first pump control unit turns on the first pump; the second pump control unit turns off the second pump, the first control unit opens the first opening / closing unit, The second control unit closes the second opening / closing unit, the third control unit opens the third opening / closing unit, The fourth control unit controls the fourth opening / closing unit to close. So, By appropriately controlling the flow rate of the second refrigerant and the opening and closing of the first, second, third, and fourth open-closed sections in accordance with the coil temperature and magnet temperature of the motor, it is possible to prevent overcooling, reduce the power consumption of the pump, and improve the cooling performance for the coil and magnet, thereby increasing the maximum torque and maximum rotation speed of the motor.

[0101] Each control unit is configured with a processor 1000 and a storage device 1010, as shown in an example of hardware in Fig. 15. Although the storage device is not shown, it includes a volatile storage device such as a random access memory and a non-volatile auxiliary storage device such as a flash memory. Furthermore, a hard disk auxiliary storage device may be provided instead of flash memory. Processor 1000 executes a program input from storage device 1010. In this case, the program is input from the auxiliary storage device to processor 1000 via a volatile storage device. Processor 1000 may output data such as calculation results to the volatile storage device of storage device 1010, or may store data in the auxiliary storage device via the volatile storage device.

[0102] While the present disclosure describes various exemplary embodiments and implementations, the various features, aspects, and functions described in one or more of the embodiments are not limited to application to a particular embodiment, but may be applied to the embodiments alone or in various combinations. Therefore, countless variations not exemplified are conceivable within the scope of the technology disclosed in this specification, including, for example, cases where at least one component is modified, added, or omitted, and cases where at least one component is extracted and combined with components of another embodiment.

[0103] Various aspects of the present disclosure are summarized below as appendices.

[0104] (Appendix 1) a motor housing portion for housing a motor; an inverter that supplies power to drive the motor; a gear housing section that houses a gear unit that transmits the output torque of the motor; the inverter is cooled by a heat exchanger through which an externally cooled first refrigerant flows; The motor housing section is a motor-side reservoir for storing a second refrigerant; a heat exchange passage that branches off from the motor-side reservoir and cools the second refrigerant through the heat exchange portion, The gear storage section is a gear-side reservoir that stores the second refrigerant that overflows from the motor-side reservoir; a gear-side passage that supplies the second refrigerant in the gear-side reservoir to the gear unit, The heat exchange passage is the passage is connected to either one or both of a coil-side passage that supplies the second refrigerant to the coil side of the motor and a magnet-side passage that supplies the second refrigerant to the magnet side of the motor; a cross-sectional area of ​​the heat exchange passage formed to be larger than the cross-sectional area of ​​the coil-side passage and the cross-sectional area of ​​the magnet-side passage; (Appendix 2) the gear storage section has a return section that returns the second refrigerant supplied from the gear-side passage to the gear unit to the motor-side reservoir section, the heat exchange passage is connected to both the coil side passage and the magnet side passage, a branching portion that branches off the coil side passage and the magnet side passage; a branch control unit for controlling a branch ratio of the branch unit; a pump that is installed on the outlet side of the heat exchange passage and circulates the second refrigerant to the coil side passage and the magnet side passage; a pump control unit that controls a discharge flow rate of the second refrigerant from the pump, The mechanically and electrically integrated drive device according to claim 1, wherein the branch control unit and the pump control unit control a flow division ratio of the second refrigerant flowing into the coil side passage and the magnet side passage and a discharge flow rate of the pump in accordance with a coil temperature and a magnet temperature of the motor. (Appendix 3) Assuming that the coil threshold temperature of the motor is Tc, the magnet threshold temperature of the motor is Tm, the coil temperature of the motor is T1, and the magnet temperature of the motor is T2, When T1 ≤ Tc, T2 ≤ Tm, the pump control unit controls the pump so that the discharge flow rate of the second refrigerant from the pump is a minimum discharge flow rate determined by the pump; 3. The mechanically and electrically integrated drive device according to claim 2, wherein the branch control unit controls the branch unit so that the entire amount of the second refrigerant flows into the coil side passage. (Appendix 4) Assuming that the coil threshold temperature of the motor is Tc, the magnet threshold temperature of the motor is Tm, the coil temperature of the motor is T1, and the magnet temperature of the motor is T2, When T1 ≥ Tc, T2 ≤ Tm, the pump control unit controls the pump to increase the discharge flow rate of the second refrigerant as the coil temperature T1 increases, The mechanically and electrically integrated drive device according to claim 2 or 3, wherein the branch control unit controls the branch unit so that the entire amount of the second refrigerant flows into the coil side passage. (Appendix 5) Assuming that the coil threshold temperature of the motor is Tc, the magnet threshold temperature of the motor is Tm, the coil temperature of the motor is T1, and the magnet temperature of the motor is T2, When T1≦Tc, T2≧Tm, As the magnet temperature T2 increases, the flow rate of the second refrigerant in the coil side passage is kept constant and the flow rate of the second refrigerant in the magnet side passage is increased. 5. The electromechanical integrated drive device according to claim 2, wherein the pump control unit and the branch control unit control the pump and the branch unit. (Appendix 6) Assuming that the coil threshold temperature of the motor is Tc, the magnet threshold temperature of the motor is Tm, the coil temperature of the motor is T1, and the magnet temperature of the motor is T2, When T1 ≥ Tc and T2 ≥ Tm, the flow rate of the second refrigerant in the coil side passage is increased as the coil temperature T1 increases, and the flow rate of the second refrigerant in the magnet side passage is increased as the magnet temperature T2 increases, 6. The electromechanical integrated drive device according to claim 2, wherein the pump control unit and the branch control unit control the pump and the branch unit. (Appendix 7) the heat exchange passage is connected to the coil side passage, the gear-side passage is connected to the magnet-side passage, a first pump that is installed on an outlet side of the heat exchange passage and that circulates the second refrigerant to the coil side passage; a first pump control unit that controls a discharge flow rate of the second refrigerant from the first pump; a second pump that is installed in the gear-side reservoir and circulates the second refrigerant to the magnet-side passage through the gear-side passage; a second pump control unit that controls a discharge flow rate of the second refrigerant from the second pump, The first pump control unit and the second pump control unit are the electromechanical integrated drive device according to appended note 1, which controls the discharge flow rates of the first pump and the second pump according to the coil temperature and the magnet temperature of the motor. (Appended note 8) Assuming that the coil threshold temperature Tc of the motor, the magnet threshold temperature Tm of the motor, the coil temperature T1 of the motor, and the magnet temperature T2 of the motor, The first pump control unit When T1 < Tc, sets the discharge flow rate of the second refrigerant of the first pump to the minimum discharge flow rate determined by the first pump, When T1 ≥ Tc, controls the discharge flow rate of the second refrigerant of the first pump to increase as the coil temperature T1 increases. The electromechanical integrated drive device according to appended note 7. (Appended note 9) Assuming that the coil threshold temperature Tc of the motor, the magnet threshold temperature Tm of the motor, the coil temperature T1 of the motor, and the magnet temperature T2 of the motor, The second pump control unit When T2 < Tm, sets the discharge flow rate of the second refrigerant of the second pump to the minimum discharge flow rate determined by the second pump, When T2 ≥ Tm, controls the discharge flow rate of the second refrigerant of the second pump to increase as the magnet temperature T2 increases. The electromechanical integrated drive device according to appended note 7 or appended note 8. (Appended note 10) The heat exchange passage is connected to the magnet side passage, The gear side passage is connected to the coil side passage, a first pump installed on the outlet side of the heat exchange passage to circulate the second refrigerant to the magnet side passage, a first pump control unit that controls the discharge flow rate of the second refrigerant of the first pump, a second pump installed in the gear side storage section to circulate the second refrigerant to the coil side passage through the gear side passage, A second pump control unit that controls the discharge flow rate of the second refrigerant of the second pump. The first pump control unit and the second pump control unit are the electromechanical integrated drive device according to Appendix 1 that controls the discharge flow rates of the first pump and the second pump according to the coil temperature and the magnet temperature of the motor. (Appendix 11) Assuming the coil threshold temperature Tc of the motor, the magnet threshold temperature Tm of the motor, the coil temperature T1 of the motor, and the magnet temperature T2 of the motor, The first pump control unit When T2 < Tm, The discharge flow rate of the second refrigerant of the first pump is set as the minimum discharge flow rate determined by the first pump. When T2 ≥ Tm, The electromechanical integrated drive device according to Appendix 10 that controls the discharge flow rate of the second refrigerant of the first pump to increase as the magnet temperature T2 increases. (Appendix 12) Assuming the coil threshold temperature Tc of the motor, the magnet threshold temperature Tm of the motor, the coil temperature T1 of the motor, and the magnet temperature T2 of the motor, The second pump control unit When T1 < Tc, The discharge flow rate of the second refrigerant of the second pump is set as the minimum discharge flow rate determined by the second pump. When T1 ≥ Tc, The electromechanical integrated drive device according to Appendix 10 or Appendix 11 that controls the discharge flow rate of the second refrigerant of the second pump to increase as the coil temperature T1 increases. (Appendix 13) The heat exchange passage is connected to both the coil side passage and the magnet side passage. The gear side passage is connected to both the coil side passage and the magnet side passage. A first opening and closing part installed on the heat exchange passage side of the magnet side passage for opening and closing the flow of the second refrigerant to the magnet side passage, A first control unit that controls the first opening and closing part, a second opening / closing unit that is installed on the gear-side passage side of the magnet-side passage and opens and closes the flow of the second refrigerant into the magnet-side passage; a second control unit that controls the second opening / closing unit; a third opening / closing unit that is installed on the heat exchange passage side of the coil side passage and opens and closes the flow of the second refrigerant into the coil side passage; a third control unit that controls the third opening / closing unit; a fourth opening / closing unit that is installed on the gear side passage side of the coil side passage and opens and closes the flow of the second refrigerant to the coil side passage; a fourth control unit that controls the fourth opening / closing unit; a first pump that is installed on an outlet side of the heat exchange passage and that circulates the second refrigerant to the coil side passage and the magnet side passage; a first pump control unit that controls the first pump to turn on and off; a second pump that is installed in the gear-side reservoir and circulates the second refrigerant to the coil-side passage and the magnet-side passage via the gear-side passage; a second pump control unit that controls the second pump to turn on and off, The electromechanical integrated drive device described in Appendix 1, wherein the first control unit, the second control unit, the third control unit, the fourth control unit, the first pump control unit, and the second pump control unit control the opening and closing of the first opening / closing unit, the second opening / closing unit, the third opening / closing unit, and the fourth opening / closing unit and the turning on and off of the first pump and the second pump in accordance with the coil temperature and magnet temperature of the motor. (Appendix 14) Assuming that the coil threshold temperature of the motor is Tc, the magnet threshold temperature of the motor is Tm, the coil temperature of the motor is T1, and the magnet temperature of the motor is T2, When T1 ≤ Tc, T2 ≤ Tm, the first pump control unit turns off the first pump, the second pump control unit turns on the second pump, The first control unit closes the first opening / closing unit, the second control unit opens the second opening / closing unit, the third control unit closes the third opening / closing unit, The electromechanical integrated drive device according to claim 13, wherein the fourth control unit controls the fourth opening / closing unit to be open. (Appendix 15) Assuming that the coil threshold temperature of the motor is Tc, the magnet threshold temperature of the motor is Tm, the coil temperature of the motor is T1, and the magnet temperature of the motor is T2, When T1 ≥ Tc, T2 ≤ Tm, the first pump control unit turns on the first pump; the second pump control unit turns on the second pump, The first control unit closes the first opening / closing unit, the second control unit opens the second opening / closing unit, the third control unit opens the third opening / closing unit, The electromechanical integrated drive device according to claim 13 or 14, wherein the fourth control unit controls the fourth opening / closing unit to close. (Appendix 16) Assuming that the coil threshold temperature of the motor is Tc, the magnet threshold temperature of the motor is Tm, the coil temperature of the motor is T1, and the magnet temperature of the motor is T2, When T1≦Tc, T2≧Tm, the first pump control unit turns on the first pump; the second pump control unit turns on the second pump, The first control unit opens the first opening / closing unit, The second control unit closes the second opening / closing unit, the third control unit closes the third opening / closing unit, 16. The electromechanical integrated drive device according to any one of Supplementary Note 13 to Supplementary Note 15, wherein the fourth control unit controls the fourth opening / closing unit to be open. (Appendix 17) Assuming that the coil threshold temperature of the motor is Tc, the magnet threshold temperature of the motor is Tm, the coil temperature of the motor is T1, and the magnet temperature of the motor is T2, When T1 ≥ Tc and T2 ≥ Tm, the first pump control unit turns on the first pump; the second pump control unit turns off the second pump, the first control unit opens the first opening / closing unit, The second control unit closes the second opening / closing unit, the third control unit opens the third opening / closing unit, The electromechanical integrated drive device according to any one of Supplementary Note 13 to Supplementary Note 16, wherein the fourth control unit controls the fourth opening / closing unit to close. (Appendix 18) The coil temperature T1 and the magnet temperature T2 are Use a value estimated using the motor input current of the motor, or The electromechanical integrated drive device according to any one of Supplementary Note 3, Supplementary Note 4, Supplementary Note 5, Supplementary Note 6, Supplementary Note 8, Supplementary Note 9, Supplementary Note 11, Supplementary Note 12, Supplementary Note 14, Supplementary Note 15, Supplementary Note 16, and Supplementary Note 17, wherein a value estimated using a motor rotation speed of the motor is used. (Appendix 19) The mechanically and electrically integrated drive device according to any one of appendices 1 to 18, wherein a fin portion is formed between the heat exchange passage and the heat exchange portion, on either the first refrigerant side or the second refrigerant side, or both. (Appendix 20) the heat exchanger is disposed below the motor-side reservoir; 20. The mechanically and electrically integrated drive device according to any one of Supplementary Note 1 to Supplementary Note 19, wherein the heat exchange passage is formed along the heat exchange portion below the motor-side reservoir portion. (Appendix 21) 21. The mechanically and electrically integrated drive device according to any one of claims 1 to 20, wherein the second refrigerant is circulated from the gear-side reservoir to the gear-side passage by a driving force of the gear unit. [Explanation of symbols]

[0105] 1 electromechanical integrated drive unit, 100 casing, 2 motor housing section, 20 motor side storage portion, 200 motor, 201 stator, 202 rotor, 203 shaft, 21 heat exchange passage, 211 coil, 212 fixed part, 22 magnet side passage, 221 magnet, 222 rotor core, 223 stator core, 23 coil side passage, 24 connecting passage, 25 pump, 251 pump control unit, 26 valve, 27 discharge section, 3 gear storage section, 30 gear side storage section, 301 gear unit, 31 gear side passage, 32 gear side pump, 321 gear side pump control unit, 33 return unit, 4 inverter, 41 heat exchange unit, 411 fin portion, 412 fin portion, 51 first valve, 511 first valve control portion, 52 second valve, 521 second valve control portion, 53 third valve, 531 third valve control section, 54 fourth valve, 541 fourth valve control section, 91 radiator, 92 electric pump, S1 flow path cross-sectional area, S2 flow path cross-sectional area, S3 flow channel cross-sectional area, H hole.

Claims

1. a motor housing portion for housing a motor; an inverter that supplies power to drive the motor; a gear housing section that houses a gear unit that transmits the output torque of the motor; the inverter is cooled by a heat exchanger through which an externally cooled first refrigerant flows, The motor housing section is a motor-side reservoir for storing a second refrigerant; a heat exchange passage that branches off from the motor-side reservoir and cools the second refrigerant through the heat exchange portion, The gear storage section is a gear-side reservoir that stores the second refrigerant that overflows from the motor-side reservoir; a gear-side passage that supplies the second refrigerant in the gear-side reservoir to the gear unit, The heat exchange passage is the passage is connected to either one or both of a coil-side passage that supplies the second refrigerant to a coil side of the motor or a magnet-side passage that supplies the second refrigerant to a magnet side of the motor; a cross-sectional area of ​​the heat exchange passage formed to be larger than the cross-sectional area of ​​the coil-side passage and the cross-sectional area of ​​the magnet-side passage;

2. the gear storage section has a return section that returns the second refrigerant supplied from the gear-side passage to the gear unit to the motor-side reservoir section, the heat exchange passage is connected to both the coil side passage and the magnet side passage, a branching portion that branches off the coil side passage and the magnet side passage; a branch control unit for controlling a branch ratio of the branch unit; a pump that is installed on an outlet side of the heat exchange passage and circulates the second refrigerant to the coil side passage and the magnet side passage; a pump control unit that controls a discharge flow rate of the second refrigerant from the pump, 2. The mechanically and electrically integrated drive device according to claim 1, wherein the branch control unit and the pump control unit control a flow division ratio of the second refrigerant flowing into the coil-side passage and the magnet-side passage and a discharge flow rate of the pump in accordance with a coil temperature and a magnet temperature of the motor.

3. Assuming that the coil threshold temperature of the motor is Tc, the magnet threshold temperature of the motor is Tm, the coil temperature of the motor is T1, and the magnet temperature of the motor is T2, When T1≦Tc and T2≦Tm, the pump control unit controls the pump so that the discharge flow rate of the second refrigerant from the pump is a minimum discharge flow rate determined by the pump; The mechanically and electrically integrated drive device according to claim 2 , wherein the branch control unit controls the branch unit so that the entire amount of the second refrigerant flows into the coil side passage.

4. Assuming that the coil threshold temperature of the motor is Tc, the magnet threshold temperature of the motor is Tm, the coil temperature of the motor is T1, and the magnet temperature of the motor is T2, When T1 ≥ Tc and T2 ≤ Tm, the pump control unit controls the pump to increase a discharge flow rate of the second refrigerant as the coil temperature T1 increases, The mechanically and electrically integrated drive device according to claim 2 , wherein the branch control unit controls the branch unit so that the entire amount of the second refrigerant flows into the coil side passage.

5. Assuming that the coil threshold temperature of the motor is Tc, the magnet threshold temperature of the motor is Tm, the coil temperature of the motor is T1, and the magnet temperature of the motor is T2, When T1≦Tc and T2≧Tm, As the magnet temperature T2 increases, the flow rate of the second refrigerant in the coil side passage is kept constant and the flow rate of the second refrigerant in the magnet side passage is increased. The electromechanical integrated drive device according to claim 2 , wherein the pump control unit and the branch unit are controlled by the pump control unit and the branch unit.

6. Assuming that the coil threshold temperature of the motor is Tc, the magnet threshold temperature of the motor is Tm, the coil temperature of the motor is T1, and the magnet temperature of the motor is T2, When T1 ≥ Tc and T2 ≥ Tm, the flow rate of the second refrigerant in the coil side passage is increased as the coil temperature T1 increases, and the flow rate of the second refrigerant in the magnet side passage is increased as the magnet temperature T2 increases, The electromechanical integrated drive device according to claim 2 , wherein the pump control unit and the branch unit are controlled by the pump control unit and the branch unit.

7. the heat exchange passage is connected to the coil side passage, the gear-side passage is connected to the magnet-side passage, a first pump disposed on an outlet side of the heat exchange passage and circulating the second refrigerant to the coil side passage; a first pump control unit that controls a discharge flow rate of the second refrigerant from the first pump; a second pump that is installed in the gear-side reservoir and circulates the second refrigerant to the magnet-side passage through the gear-side passage; a second pump control unit that controls a discharge flow rate of the second refrigerant from the second pump, 2. The electromechanical integrated drive device according to claim 1, wherein the first pump control unit and the second pump control unit control the discharge flow rates of the first pump and the second pump in accordance with the coil temperature and magnet temperature of the motor.

8. Assuming that the coil threshold temperature of the motor is Tc, the magnet threshold temperature of the motor is Tm, the coil temperature of the motor is T1, and the magnet temperature of the motor is T2, The first pump control unit If T1<Tc, a discharge flow rate of the second refrigerant from the first pump is set to a minimum discharge flow rate determined by the first pump; If T1 ≥ Tc, 8. The mechanically and electrically integrated drive device according to claim 7, wherein the discharge flow rate of the second refrigerant from the first pump is controlled to increase as the coil temperature T1 increases.

9. Assuming that the coil threshold temperature of the motor is Tc, the magnet threshold temperature of the motor is Tm, the coil temperature of the motor is T1, and the magnet temperature of the motor is T2, The second pump control unit If T2<Tm, a discharge flow rate of the second refrigerant from the second pump is a minimum discharge flow rate determined by the second pump; If T2 ≥ Tm, 8. The electromechanical integrated drive device according to claim 7, wherein the discharge flow rate of the second refrigerant from the second pump is controlled to increase as the magnet temperature T2 increases.

10. the heat exchange passage is connected to the magnet side passage, the gear-side passage is connected to the coil-side passage, a first pump that is installed on an outlet side of the heat exchange passage and that circulates the second refrigerant to the magnet side passage; a first pump control unit that controls a discharge flow rate of the second refrigerant from the first pump; a second pump installed in the gear-side reservoir and configured to circulate the second refrigerant to the coil-side passage via the gear-side passage; a second pump control unit that controls a discharge flow rate of the second refrigerant from the second pump, 2. The electromechanical integrated drive device according to claim 1, wherein the first pump control unit and the second pump control unit control the discharge flow rates of the first pump and the second pump in accordance with the coil temperature and magnet temperature of the motor.

11. Assuming that the coil threshold temperature of the motor is Tc, the magnet threshold temperature of the motor is Tm, the coil temperature of the motor is T1, and the magnet temperature of the motor is T2, The first pump control unit If T2<Tm, a discharge flow rate of the second refrigerant from the first pump is a minimum discharge flow rate determined by the first pump; If T2 ≥ Tm, 11. The electromechanical integrated drive device according to claim 10, wherein the discharge flow rate of the second refrigerant from the first pump is controlled to increase as the magnet temperature T2 increases.

12. Assuming that the coil threshold temperature of the motor is Tc, the magnet threshold temperature of the motor is Tm, the coil temperature of the motor is T1, and the magnet temperature of the motor is T2, The second pump control unit If T1<Tc, a discharge flow rate of the second refrigerant from the second pump is a minimum discharge flow rate determined by the second pump; When T1 ≥ Tc, The electromechanical integrated drive device according to claim 10, wherein the discharge flow rate of the second refrigerant from the second pump is controlled to increase as the coil temperature T1 increases.

13. the heat exchange passage is connected to both the coil side passage and the magnet side passage, the gear-side passage is connected to both the coil-side passage and the magnet-side passage, a first opening / closing unit that is installed on the heat exchange passage side of the magnet-side passage and opens and closes the flow of the second refrigerant into the magnet-side passage; a first control unit that controls the first opening / closing unit; a second opening / closing unit that is installed on the gear-side passage side of the magnet-side passage and opens and closes the flow of the second refrigerant into the magnet-side passage; a second control unit that controls the second opening / closing unit; a third opening / closing unit that is installed on the heat exchange passage side of the coil side passage and opens and closes the flow of the second refrigerant into the coil side passage; a third control unit that controls the third opening / closing unit; a fourth opening / closing unit that is installed on the gear-side passage side of the coil-side passage and opens and closes the flow of the second refrigerant into the coil-side passage; a fourth control unit that controls the fourth opening / closing unit; a first pump that is installed on an outlet side of the heat exchange passage and that circulates the second refrigerant to the coil side passage and the magnet side passage; a first pump control unit that controls ON / OFF of the first pump; a second pump that is installed in the gear-side reservoir and circulates the second refrigerant to the coil-side passage and the magnet-side passage via the gear-side passage; a second pump control unit that controls ON / OFF of the second pump, 2. The electromechanical integrated drive device according to claim 1, wherein the first control unit, the second control unit, the third control unit, the fourth control unit, the first pump control unit, and the second pump control unit control the opening and closing of the first opening / closing unit, the second opening / closing unit, the third opening / closing unit, and the fourth opening / closing unit and the turning on and off of the first pump and the second pump in accordance with the coil temperature and the magnet temperature of the motor.

14. Assuming that the coil threshold temperature of the motor is Tc, the magnet threshold temperature of the motor is Tm, the coil temperature of the motor is T1, and the magnet temperature of the motor is T2, When T1≦Tc and T2≦Tm, the first pump control unit turns off the first pump; the second pump control unit turns on the second pump, The first control unit closes the first opening / closing unit, the second control unit opens the second opening / closing unit, the third control unit closes the third opening / closing unit, The electromechanical integrated drive device according to claim 13 , wherein the fourth control unit controls the fourth opening / closing unit to be open.

15. Assuming that the coil threshold temperature of the motor is Tc, the magnet threshold temperature of the motor is Tm, the coil temperature of the motor is T1, and the magnet temperature of the motor is T2, When T1 ≥ Tc and T2 ≤ Tm, the first pump control unit turns on the first pump; the second pump control unit turns on the second pump, The first control unit closes the first opening / closing unit, the second control unit opens the second opening / closing unit, the third control unit opens the third opening / closing unit, The electromechanical integrated drive device according to claim 13 , wherein the fourth control unit controls the fourth opening / closing unit to close.

16. Assuming that the coil threshold temperature of the motor is Tc, the magnet threshold temperature of the motor is Tm, the coil temperature of the motor is T1, and the magnet temperature of the motor is T2, When T1≦Tc and T2≧Tm, the first pump control unit turns on the first pump; the second pump control unit turns on the second pump, The first control unit opens the first opening / closing unit, The second control unit closes the second opening / closing unit, the third control unit closes the third opening / closing unit, The electromechanical integrated drive device according to claim 13 , wherein the fourth control unit controls the fourth opening / closing unit to be open.

17. Assuming that the coil threshold temperature of the motor is Tc, the magnet threshold temperature of the motor is Tm, the coil temperature of the motor is T1, and the magnet temperature of the motor is T2, When T1 ≥ Tc and T2 ≥ Tm, the first pump control unit turns on the first pump; the second pump control unit turns off the second pump; the first control unit opens the first opening / closing unit, The second control unit closes the second opening / closing unit, the third control unit opens the third opening / closing unit, The electromechanical integrated drive device according to claim 13 , wherein the fourth control unit controls the fourth opening / closing unit to close.

18. The coil temperature T1 and the magnet temperature T2 are Use a value estimated using the motor input current of the motor, or The electromechanical integrated drive device according to any one of claims 3, 4, 5, 6, 8, 9, 11, 12, 14, 15, 16, and 17, wherein a value estimated using the motor rotation speed of the motor is used.

19. 18. The mechanically and electrically integrated drive device according to claim 1, wherein a fin portion is formed between the heat exchange passage and the heat exchange portion, on either the first refrigerant side or the second refrigerant side, or both.

20. the heat exchanger is disposed below the motor-side reservoir; 18. The mechanically and electrically integrated drive device according to claim 1, wherein the heat exchange passage is formed below the motor-side reservoir along the heat exchange portion.

21. The mechanically and electrically integrated drive device according to any one of claims 1 to 17, wherein the second refrigerant is circulated from the gear-side reservoir to the gear-side passage by a driving force of the gear unit.

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