JP2023152267A - Heat pump device for moving body - Google Patents

Abstract

To provide a heat pump device for a moving body that can preferably cool an inverter circuit and has excellent mountability to a moving body.SOLUTION: A heat pump device is equipped with an electric compressor 1, a condenser 9, and an evaporator 11. The electric compressor 1 has a housing 10, a compression mechanism 16, an inverter circuit 18, a suction port 16a, a discharge port 16b, and the like. In the heat pump device, the electric compressor 1 is disposed between the condenser 9 and the evaporator 11, and the condenser 9, the electric compressor 1, and the evaporator 11 are integrated. The inverter circuit 18 is disposed between the compression mechanism 16 and the evaporator 11. The discharge port 16b is disposed closer to the condenser 9 than the suction port 16a, and the suction port 16a is disposed closer to the evaporator 11 than the discharge port 16b.SELECTED DRAWING: Figure 1

Description

The present invention relates to a heat pump device for a mobile body.

Patent Document 1 discloses a conventional heat pump device for a moving object (hereinafter simply referred to as a heat pump device). This heat pump device is mounted on an electric vehicle as a moving body. The heat pump device includes an electric compressor, a condenser, and an evaporator.

An electric compressor consists of a housing, a suction port that sucks in refrigerant, a discharge port that discharges refrigerant, a compression mechanism that compresses the refrigerant sucked in from the suction port and discharges it from the discharge port, and an electric motor that operates the compression mechanism. and an inverter circuit that controls the electric motor. The compression mechanism, electric motor and inverter circuit are provided within the housing. Here, in this document, the specific locations where the suction port and the discharge port are arranged are unclear.

The condenser exchanges heat between the refrigerant and the heating liquid. The condenser has a first inlet through which the refrigerant discharged from the discharge port flows, and a first outlet through which the refrigerant flows out toward the evaporator. The evaporator exchanges heat between the refrigerant and the cooling liquid. The evaporator has a second inlet into which the refrigerant flowing out from the first outlet flows, and a second outlet into which the refrigerant flows out toward the suction port.

In this heat pump device, the housing and the evaporator are integrated in the radial direction of the housing. Thereby, the condenser is arranged on the outer peripheral side of the compression mechanism and the electric motor. On the other hand, the evaporator is integrated with the housing in the axial direction of the housing. Note that the radial direction of the housing and the axial direction of the housing are perpendicular to each other. Moreover, the inverter circuit is arranged between the compression mechanism and the evaporator.

In this heat pump device, the heating liquid is heated by heat exchange between the refrigerant and the heating liquid in the condenser. Further, the cooling liquid is cooled by heat exchange between the refrigerant and the cooling liquid in the evaporator. The heating liquid heated in the condenser is used to heat the interior of the vehicle. On the other hand, the cooling liquid cooled by the evaporator is used to cool the driving motor and the like. Further, in this heat pump device, the inverter circuit can be cooled by a low-temperature evaporator.

Japanese Patent Application Publication No. 2014-125157

By the way, since various devices other than the heat pump device are mounted on the moving body, it is difficult to secure a sufficient space for mounting the heat pump device. Therefore, even if the mounting space is limited in this way, the heat pump device is required to be able to be easily mounted on a moving body.

The present invention has been made in view of the above-mentioned conventional circumstances, and an object of the present invention is to provide a heat pump device for a mobile body that can suitably cool an inverter circuit and is easy to mount on a mobile body. This is an issue that should be addressed.

The heat pump device for a mobile body of the present invention includes a housing, an inlet provided in the housing for sucking in a refrigerant, a discharge port provided in the housing for discharging the refrigerant, and a suction port provided in the housing for sucking in the refrigerant. an electric compressor having a compression mechanism that discharges refrigerant sucked in through the mouth from the discharge port; and an electric motor that is provided in the housing and operates the compression mechanism;
a condenser that exchanges heat between the refrigerant and the heating liquid;
Equipped with an evaporator that exchanges heat between the refrigerant and the cooling liquid,
The condenser has a first inlet that allows the refrigerant discharged from the outlet to flow in, and a first outlet that allows the refrigerant to flow out toward the evaporator.
The evaporator is a heat pump device for a mobile body, which has a second inlet into which the refrigerant flowing out from the first outflow port flows, and a second outflow port into which the refrigerant flows out toward the suction port. hand,
The electric compressor is disposed between the condenser and the evaporator, and the condenser, the electric compressor, and the evaporator are integrated,
The electric compressor further includes an inverter circuit provided in the housing and controlling the electric motor,
the inverter circuit is arranged between the compression mechanism and the evaporator,
The discharge port is located closer to the condenser than the suction port,
The suction port is located closer to the evaporator than the discharge port.

In the heat pump device for a mobile object of the present invention, the electric compressor is disposed between the condenser and the evaporator, and the condenser, electric compressor, and evaporator are integrated. Here, in this heat pump device, the condenser, the housing, and the evaporator are integrated, so that the inverter circuit is disposed between the compression mechanism and the evaporator. Therefore, the inverter circuit can be suitably cooled by the low-temperature evaporator.

In this heat pump device, the discharge port is located closer to the condenser than the suction port, and the suction port is located closer to the evaporator than the discharge port. For this reason, for example, compared to a case where the discharge port is located farther from the condenser than the suction port, in this heat pump device, the refrigerant discharged from the discharge port reaches the first inlet of the condenser. The distance can be shortened. Similarly, the distance that the refrigerant flowing out from the second outlet of the evaporator reaches the suction port can also be shortened. Thereby, this heat pump device can suppress the increase in size as a whole.

Therefore, the heat pump device for a moving object of the present invention can suitably cool an inverter circuit, and has excellent mountability on a moving object.

The first outlet and the second inlet may be connected by a circulation passage. Preferably, at least a portion of the circulation passage is formed in the housing. In this case, compared to a configuration in which all of the circulation passages are provided outside the housing and separate from the housing, the heat pump device can be more easily mounted on the moving body.

The circulation passage may be provided with a gas-liquid separator and a throttle section that is located downstream of the gas-liquid separator in the refrigerant flow direction and reduces the pressure of the refrigerant flowing through the circulation passage. The gas-liquid separator is preferably disposed between the housing and the condenser.

Further, the circulation passage may be provided with a gas-liquid separator and a throttle section that is located downstream of the gas-liquid separator in the refrigerant flow direction and reduces the pressure of the refrigerant flowing through the circulation passage. It is also preferable that the condenser is disposed between the gas-liquid separator and the electric compressor.

Further, the circulation passage may be provided with a gas-liquid separator and a throttle section that is located downstream of the gas-liquid separator in the refrigerant flow direction and reduces the pressure of the refrigerant flowing through the circulation passage. It is also preferable that the gas-liquid separator is disposed between the housing and the evaporator.

Further, the circulation passage may be provided with a gas-liquid separator and a throttle section that is located downstream of the gas-liquid separator in the refrigerant flow direction and reduces the pressure of the refrigerant flowing through the circulation passage. It is also preferable that the gas-liquid separator is disposed within the housing.

In these cases, although the gas-liquid separator and the throttle section are provided in the circulation path, the heat pump device can be easily mounted on the moving body.

The condenser includes a first refrigerant region on the condenser side that is connected to the first inlet, and a first refrigerant region on the condenser side that is located downstream of the first refrigerant region on the condenser side in the flow direction of the refrigerant and connected to the first outlet. a second refrigerant region; a condenser located between the first refrigerant region on the condenser side and the second refrigerant region on the condenser side and connected to the first refrigerant region on the condenser side and the second refrigerant region on the condenser side; and a side gas-liquid separation section. Further, the refrigerant flowing through the first refrigerant region on the condenser side and the refrigerant flowing through the second refrigerant region on the condenser side can exchange heat with the heating liquid. It is also preferable that the circulation passage is provided with a constriction part that reduces the pressure of the refrigerant flowing through the circulation passage.

In this case, the refrigerant that has been subjected to gas-liquid separation by the condenser-side gas-liquid separation section flows through the condenser-side second refrigerant region. Therefore, the refrigerant flowing through the second refrigerant region on the condenser side can be suitably supercooled by heat exchange with the heating liquid. Thereby, the refrigerant flowing out from the first outlet and flowing through the circulation passage toward the throttle part, that is, the refrigerant before being depressurized by the throttle part, can be turned into a liquid phase with high reliability. As a result, the generation of gas phase refrigerant at the second inlet of the evaporator can be suitably suppressed, so that the cooling liquid can be suitably cooled by heat exchange in the evaporator.

In the heat pump device of the present invention, the suction port and the second outlet may be connected by a suction passage. Further, the circulation passage may be provided with a constriction portion that reduces the pressure of the refrigerant flowing through the circulation passage. The heat pump device of the present invention includes a circulation path side detection section that is provided inside the housing and connected to the inverter circuit, and that detects the pressure of the refrigerant flowing upstream of the constriction section in the circulation path; Preferably, the refrigerant refrigerant further includes a suction passage-side detection unit that is connected to the inverter circuit and detects the pressure and temperature of the refrigerant flowing through the suction passage.

In this case, the inverter can control the electric motor based on the pressure of the refrigerant flowing through the circulation passage and the pressure and temperature of the refrigerant flowing through the suction passage. Thereby, in this heat pump device for a mobile object, it is possible to suitably prevent the electric compressor from operating with the refrigerant at an excessively high pressure, and the liquid phase refrigerant being sucked into the compression mechanism.

Moreover, in this case, it is preferable that the circulation passage side detection part detects the temperature of the refrigerant flowing upstream of the throttle part in the circulation passage. Thereby, the inverter can control the electric motor more appropriately.

In the heat pump device of the present invention, an accumulator may be provided between the second outlet and the suction port. Furthermore, the circulation passage may be provided with a fixed throttle which reduces the passage area of the circulation passage. And it is also preferable that the accumulator is arranged between the housing and the evaporator.

Furthermore, an accumulator may be provided between the second outlet and the inlet. Furthermore, the circulation passage may be provided with a fixed throttle which reduces the passage area of the circulation passage. It is also preferable that the evaporator is disposed between the accumulator and the electric compressor.

Furthermore, an accumulator may be provided between the second outlet and the inlet. Furthermore, the circulation passage may be provided with a fixed throttle which reduces the passage area of the circulation passage. It is also preferable that the accumulator is disposed within the housing.

In these cases, although the accumulator is provided, the heat pump device can be easily mounted on the moving body.

The heat pump device of the present invention includes a high-pressure side detection section that is provided in the housing and connected to the inverter circuit, and detects the pressure of the refrigerant flowing upstream of the fixed throttle in the circulation passage; It is also preferable to further include a low-pressure side detection section that is connected to the circuit and detects the pressure and temperature of the refrigerant flowing between the accumulator and the suction port.

In this case as well, the inverter circuit can control the electric motor in a suitable manner, preventing the electric compressor from operating when the refrigerant is at an excessively high pressure, and preventing liquid-phase refrigerant from being sucked into the compression mechanism. This can be suitably prevented.

Further, it is preferable that the high-pressure side detection section detects the temperature of the refrigerant flowing upstream of the fixed throttle in the circulation passage. Thereby, the inverter can control the electric motor more appropriately.

The evaporator includes an evaporator-side first refrigerant region located downstream in the refrigerant flow direction than the second inlet, and a evaporator-side first refrigerant region located downstream in the refrigerant flow direction than the evaporator-side first refrigerant region. a second refrigerant region on the evaporator side connected to the first refrigerant region on the evaporator side and the second outlet; an evaporator-side gas-liquid separation section connected to the evaporator-side first refrigerant region; and an evaporator-side gas-liquid separation section connected to the evaporator-side first refrigerant region; The evaporator may have an evaporator-side constriction section that reduces the pressure of the refrigerant that flows through the evaporator. The refrigerant flowing through the evaporator-side first refrigerant region and the refrigerant flowing through the evaporator-side second refrigerant region preferably exchange heat with the cooling liquid.

In this case, the refrigerant flowing from the second inlet is separated into gas and liquid by the evaporator-side gas-liquid separation section, and then flows through the evaporator-side first refrigerant region. Therefore, the refrigerant flowing through the first refrigerant region on the evaporator side can be suitably supercooled by heat exchange with the cooling liquid. Thereby, the refrigerant that has passed through the first refrigerant region on the evaporator side, that is, the refrigerant before being depressurized in the evaporator-side throttle section, can be turned into a liquid phase with high reliability. As a result, since the pressure of the refrigerant can be suitably reduced in the evaporator-side throttle section, the cooling liquid can be suitably cooled by heat exchange with the refrigerant flowing through the second evaporator-side refrigerant region.

The evaporator also includes an evaporator-side first refrigerant region located downstream of the second inlet in the refrigerant flow direction, and a first evaporator-side refrigerant region located downstream of the evaporator-side first refrigerant region in the refrigerant flow direction. , an evaporator-side second refrigerant region connected to the evaporator-side first refrigerant region; a third refrigerant region on the evaporator side that is connected to the outlet; and a third refrigerant region on the evaporator side that is located upstream in the flow direction of the refrigerant than the first refrigerant region on the evaporator side and connected to the second inlet and the first refrigerant region on the evaporator side. the evaporator-side gas-liquid separation section, which is located between the evaporator-side first refrigerant region and the evaporator-side second refrigerant region, and which reduces the pressure of the refrigerant flowing through the evaporator-side first refrigerant region. It may have a constriction part. Furthermore, the refrigerant flowing through the first refrigerant region on the evaporator side can exchange heat with the refrigerant flowing through the third refrigerant region on the evaporator side. It is also preferable that the refrigerant flowing through the second refrigerant region on the evaporator side exchanges heat with the cooling liquid.

In this case, in the evaporator, the refrigerant that has flowed in from the second inlet is separated into gas and liquid by the evaporator-side gas-liquid separation section, so that liquid-phase refrigerant flows through the evaporator-side first refrigerant region. Further, the refrigerant flowing through the first refrigerant region on the evaporator side exchanges heat with the refrigerant flowing through the third refrigerant region on the evaporator side. Therefore, the refrigerant flowing through the first refrigerant region on the evaporator side can be suitably supercooled. Thereby, the refrigerant that has passed through the first refrigerant region on the evaporator side, that is, the refrigerant before being depressurized in the evaporator-side throttle section, can be turned into a liquid phase with high reliability. As a result, the refrigerant is suitably depressurized in the evaporator-side constriction section and flows through the evaporator-side second refrigerant region, so that the cooling liquid can be suitably cooled by heat exchange with the cooling liquid. can.

The housing includes a heating liquid inlet that allows heating liquid to flow into the condenser, a heating liquid outlet that allows heating liquid to flow out of the condenser, a cooling liquid inlet that allows cooling liquid to flow into the evaporator, and a cooling liquid inlet that allows heating liquid to flow into the evaporator. Preferably, a cooling liquid outlet is formed for allowing cooling liquid to exit the evaporator.

In this case, a space for forming a heating liquid inlet and a heating liquid outlet for the condenser is not required, and a space for forming a cooling liquid inlet and a cooling liquid outlet for the evaporator is not required. No space is needed. Therefore, the condenser and evaporator can be downsized. Moreover, a dedicated member provided with a heating liquid inlet, a heating liquid outlet, a cooling liquid inlet, and a cooling liquid outlet is also unnecessary. For these reasons, the heat pump device can be more easily mounted on a moving object.

At least one of the evaporator and the condenser may include a plurality of heat exchange plates and a spacer disposed between each heat exchange plate. Moreover, each heat exchange plate, spacer, and housing may be integrally fastened by a fastening member. Preferably, the space between each heat exchange plate and the spacer is sealed by the fastening force of the fastening member.

In this case, it is possible to suitably perform heat exchange between the heating liquid or the cooling liquid and the refrigerant while simplifying the configuration of at least one of the condenser and the evaporator. Additionally, if the condenser has heat exchange plates and spacers, the condenser and housing can be integrally fastened in the process of fastening each heat exchange plate, spacer, and housing with the fastening member. becomes. Furthermore, by sealing between each heat exchange plate and the spacer by the fastening force of the fastening member, leakage of the refrigerant as well as the heating liquid and the cooling liquid can be suitably suppressed.

Preferably, the electric motor is arranged between the compression mechanism and the inverter circuit. In this case, the electric motor can also be suitably cooled by the low-temperature evaporator. Further, since the inverter circuit and the electric motor can be arranged close to each other, the connection between the inverter circuit and the electric motor can be facilitated.

The discharge port and the first inlet may be connected by a discharge passage. Further, the suction port and the second outlet may be connected by a suction passage. Preferably, at least a portion of the discharge passage and the suction passage is formed in the housing. In this case, the heat pump device can be more easily mounted on the moving body than a configuration in which the discharge passage and the suction passage are all separate from the housing and provided outside the housing.

The heat pump device for a mobile body of the present invention can suitably cool an inverter circuit, and has excellent mountability on a mobile body.

FIG. 1 is a side view of a heat pump device for a moving body according to a first embodiment. FIG. 2 is a schematic diagram of the heat pump device for a moving body according to the first embodiment. FIG. 3 is an enlarged cross-sectional view of a main part showing the X portion in FIG. FIG. 4 is a schematic diagram of a heat pump device for a moving body according to a second embodiment. FIG. 5 is a schematic diagram of a heat pump device for a mobile object according to Example 3. FIG. 6 is a schematic diagram of a heat pump device for a mobile object according to Example 4. FIG. 7 is a schematic diagram of a heat pump device for a mobile object according to Example 5. FIG. 8 is a schematic diagram of a heat pump device for a mobile object according to Example 6. FIG. 9 is a schematic diagram of a heat pump device for a moving body according to Example 7. FIG. 10 is a schematic diagram of a heat pump device for a moving body according to Example 8. FIG. 11 is a schematic diagram of a heat pump device for a mobile object according to Example 9. FIG. 12 is a schematic diagram of a heat pump device for a moving body according to Example 10.

Examples 1 to 10 embodying the present invention will be described below with reference to the drawings.

(Example 1)
As shown in FIGS. 1 and 2, the heat pump device of Example 1 includes an electric compressor 1, a receiver case 3, a receiver 5, an expansion valve 7, a condenser 9, an evaporator 11, and a control device. (not shown). The heat pump device of Example 1 is mounted on an electric vehicle 100. Electric vehicle 100 is an example of a "mobile object" in the present invention. Further, the receiver 5 is an example of a "gas-liquid separator" in the present invention. The expansion valve 7 is an example of the "throttle part" in the present invention. Note that in FIG. 1, illustration of the expansion valve 7 is omitted.

The electric compressor 1 includes a compressor housing 13, a motor housing 14, an inverter housing 15, a compression mechanism 16, an electric motor 17, and an inverter circuit 18. A housing 10 is constituted by a compressor housing 13, a motor housing 14, and an inverter housing 15. The housing 10 is made of metal such as aluminum alloy.

In this embodiment, the axial direction D1 of the housing 10 is indicated by the solid arrow shown in FIG. 1 and the like. Furthermore, in this embodiment, one side in the axial direction D1 will be described as the D1A side, and the other side in the axial direction D1 will be described as the D1B side.

As shown in FIG. 1, the compressor housing 13 includes a main body portion 131 and a fixing portion 133. The main body portion 131 has a substantially cylindrical shape extending in the axial direction D1. The fixing part 133 is integrated with the main body part 131 on the D1A side of the main body part 131. That is, in the compressor housing 13, the main body portion 131 constitutes the D1B side of the compressor housing 13, and the fixed portion 133 constitutes the D1A side of the compressor housing 13. The main body portion 131 and the fixing portion 133 communicate internally.

The compressor housing 13 is provided with an inlet 16a and an outlet 16b. More specifically, the suction port 16a and the discharge port 16b are each provided in the main body portion 131. Here, the suction port 16a is located closer to the D1B side than the discharge port 16b in the main body portion 131. That is, the suction port 16a is located on the D1B side of the compressor housing 13, and the discharge port 16b is located on the D1A side of the compressor housing 13.

Further, as shown in FIG. 2, the compressor housing 13 is formed with a first discharge passage 21a, a third circulation passage 22c, and a third suction passage 23c. Here, the first discharge passage 21a and the third circulation passage 22c are formed across the main body part 131 and the fixed part 133. The third suction passage 23c is formed only in the main body portion 131. Refrigerant can flow through the first discharge passage 21a, the third circulation passage 22c, and the third suction passage 23c.

Further, the compressor housing 13 is formed with a heating liquid inlet 31, a heating liquid outlet 32, a first heating liquid passage 33a, and a fourth heating liquid passage 33d. The heating liquid inlet 31 and the heating liquid outlet 32 are formed at different positions in the fixed portion 133 and open to the outside of the compressor housing 13 . The first heating liquid passage 33a and the fourth heating liquid passage 33d are formed in the fixed portion 133. The first heating liquid passage 33a is connected to the heating liquid inlet 31. The fourth heating liquid passage 33d is connected to the heating liquid outlet 32.

Pipes (not shown) are connected to the heating liquid inlet 31 and the heating liquid outlet 32, respectively. Thereby, heating liquid flows into the heating liquid inlet 31 from the outside of the heat pump device into the fixing part 133 and eventually into the housing 10 through the piping. Further, the heating liquid flows out from the housing 10 to the outside of the heat pump device through the heating liquid outlet 32 and the piping. Here, a long-life coolant is used as the heating liquid.

Although not shown, the fixed portion 133 is provided with a partition wall. Due to this partition wall, the heating liquid that flows in from the heating liquid inlet 31 and the heating liquid that flows out from the heating liquid outlet 32 do not mix within the fixed part 133 .

As shown in FIG. 1, the motor housing 14, like the main body portion 131 of the compressor housing 13, has a substantially cylindrical shape extending in the axial direction D1. The inverter housing 15 is integrated with the motor housing 14 on the D1B side of the motor housing 14.

As shown in FIG. 2, the motor housing 14 is formed with a fourth circulation passage 22d and a second suction passage 23b. The inverter housing 15 is formed with a fifth circulation passage 22e and a first suction passage 23a. The fifth circulation passage 22e is connected to the D1B side of the fourth circulation passage 22d on the D1A side. The first suction passage 23a is connected on the D1A side to the D1B side of the second suction passage 23b.

Further, the inverter housing 15 is formed with a cooling liquid inlet 34, a cooling liquid outlet 35, a first cooling liquid passage 36a, and a second cooling liquid passage 36b. The cooling liquid inlet 34 and the cooling liquid outlet 35 are formed at different positions in the inverter housing 15 and open to the outside of the inverter housing 15. The first cooling liquid passage 36a is connected to the cooling liquid inlet 34. The second cooling liquid passage 36b is connected to the cooling liquid outlet 35.

Piping (not shown) is connected to the cooling liquid inlet 34 and the cooling liquid outlet 35, respectively. Thereby, the cooling liquid flows into the inverter housing 15 and eventually into the housing 10 from the outside of the heat pump device through the cooling liquid inlet 34 and the piping. Further, the cooling liquid flows out from the inside of the housing 10 to the outside of the heat pump device through the cooling liquid outlet 35 and the piping. Here, a long-life coolant is used for the cooling liquid as well as the heating liquid. Note that the heating liquid and the cooling liquid may be water or the like.

Although not shown, the inverter housing 15 is provided with a partition wall, and the partition wall prevents the cooling liquid from coming into direct contact with an inverter circuit 18, which will be described later, within the inverter housing 15. Moreover, the partition wall prevents the cooling liquid flowing in from the cooling liquid inlet 34 and the cooling liquid flowing out from the cooling liquid outlet 35 from mixing within the inverter housing 15 .

The compression mechanism 16 is housed within the main body portion 131 of the compressor housing 13. Although not shown in detail, the compression mechanism 16 is a known scroll type compression mechanism. The compression mechanism 16 is connected to an inlet 16a and an outlet 16b. Further, the suction port 16a is connected to the D1A side of the third suction passage 23c. The discharge port 16b is connected to the D1B side of the first discharge passage 21a. Thereby, the compression mechanism 16 is connected to the third suction passage 23c through the suction port 16a, and connected to the first discharge passage 21a through the discharge port 16b. Note that instead of the scroll type compression mechanism, a swash plate type compression mechanism, a vane type compression mechanism, or the like may be employed as the compression mechanism 16.

Electric motor 17 is housed within motor housing 14 . Although detailed illustrations are omitted, the electric motor 17 is composed of a known stator, rotor, and the like.

Inverter circuit 18 is housed within inverter housing 15 . Thereby, the inverter circuit 18 is located on the D1B side with respect to the electric motor 17 housed in the motor housing 14. That is, the inverter circuit 18 is adjacent to the electric motor 17 in the axial direction D1 within the housing 10.

Although detailed illustrations are omitted, the inverter circuit 18 is composed of a circuit board, switching elements provided on the circuit board, and the like. The inverter circuit 18 is electrically connected to the electric motor 17 . Further, the inverter circuit 18 is connected to a connector portion (not shown) provided on the inverter housing 15. Thereby, the inverter circuit 18 is electrically connected to a battery (not shown) of the electric vehicle 100 through the connector portion. Further, the inverter circuit 18 is connected to a control device (not shown).

As shown in FIG. 1, the motor housing 14 and the inverter housing 15 are arranged on the D1B side with respect to the compressor housing 13. The main body portion 131 of the compressor housing 13 and the motor housing 14 are opposed to each other in the axial direction D1, and the compressor housing 13 and the motor housing 14 are fastened together by bolts (not shown). Thereby, the compressor housing 13 and the motor housing 14 are fixed in the axial direction D1. Thus, in the housing 10, the compressor housing 13, the motor housing 14, and the inverter housing 15 are arranged in this order in the axial direction D1. That is, in the housing 10, the compressor housing 13 is located closest to the D1A side, and the inverter housing 15 is located closest to the D1B side.

Moreover, within the housing 10, the compression mechanism 16, the electric motor 17, and the inverter circuit 18 are arranged in this order in the axial direction D1. That is, the inverter circuit 18 is disposed closest to the D1B side, and the electric motor 17 is disposed between the compression mechanism 16 and the inverter circuit 18. The compression mechanism 16 and the electric motor 17 are connected so that power can be transmitted.

Further, by fixing the compressor housing 13 and the motor housing 14 in the axial direction D1, the D1B side of the third circulation passage 22c and the D1A side of the fourth circulation passage 22d are connected. Thereby, the third circulation passage 22c, the fourth circulation passage 22d, and the fifth circulation passage 22e are connected. Further, the D1B side of the third suction passage 23c and the D1A side of the second suction passage 23b are connected. Thereby, the first suction passage 23a, the second suction passage 23b, and the third suction passage 23c are connected.

Further, as described above, since the discharge port 16b is located on the D1A side of the compressor housing 13, the discharge port 16b is located on the D1A side of the housing 10. On the other hand, the suction port 16a is located on the D1B side of the housing 10, more precisely, the suction port 16a is located on the D1A side of the housing 10 rather than the discharge port 16b.

The receiver case 3 is formed into a substantially rectangular box shape. The receiver case 3 is arranged on the D1A side of the fixed portion 133 of the compressor housing 13. That is, the receiver case 3 is arranged in the axial direction D1 with respect to the housing 10 and, by extension, the electric compressor 1, and is located on the D1A side of the electric compressor 1.

As shown in FIG. 2, the receiver case 3 is formed with a second discharge passage 21b, a first circulation passage 22a, and a second circulation passage 22b, as well as a second heating liquid passage 33b and a second heating liquid passage 33b. 3 heating liquid passages 33c are formed.

The receiver 5 and the expansion valve 7 are housed within the receiver case 3. The receiver 5 is located between the first circulation passage 22a and the second circulation passage 22b, and is connected to the first circulation passage 22a and the second circulation passage 22b. The expansion valve 7 is provided in the second circulation passage 22b. Further, the expansion valve 7 is connected to a control device (not shown). Note that the receiver 5 and the expansion valve 7 have the same configuration as a known receiver and expansion valve, respectively, so detailed explanations will be omitted. Further, by being housed in the housing 10, the expansion valve 7 may be provided in any of the third to fifth circulation passages 22c to 22e instead of the second circulation passage 22b.

As shown in FIGS. 1 and 3, the condenser 9 includes a plurality of first heat exchange plates 91, a plurality of first spacers 92, one first end plate 93, and one second It is composed of an end plate 94. Each first heat exchange plate 91 is an example of a "heat exchange plate" in the present invention. Further, each first spacer 92 is an example of a "spacer" in the present invention.

Each of the first heat exchange plates 91, each of the first spacers 92, and the first and second end plates 93 and 94 are made of metal and are formed into a substantially rectangular plate shape. Each of the first heat exchange plates 91 and each of the first spacers 92 is thinner than the first and second end plates 93 and 94. As shown in FIG. 3, each first spacer 92 is provided with resin seal members 921 and 922 on both surfaces in the axial direction D1, respectively.

The first end plate 93 is disposed closest to the D1A side in the condenser 9. The second end plate 94 is located closest to D1B in the condenser 9. Each first heat exchange plate 91 and first spacer 92 is arranged between the first end plate 93 and the second end plate 94.

Here, each of the first heat exchange plates 91 and each of the first spacers 92 are arranged alternately in the axial direction D1. That is, the first spacer 92 is arranged between the first heat exchange plates 91 in the axial direction D1. Thereby, the first heat exchange plates 91 are separated from each other in the axial direction D1 by the first spacer 92.

Also, between the first heat exchange plate 91 and the first end plate 93 located closest to the D1A side, and between the first heat exchange plate 91 and the second end plate 94 located closest to the D1B side, They are separated in the axial direction D1 by a first spacer 92.

Then, between the first heat exchange plates 91, between the first heat exchange plate 91 located closest to the D1A side and the first end plate 93, and between the first heat exchange plate 91 located closest to the D1B side and the first end plate 93, A first refrigerant region 91a into which a refrigerant flows or a first liquid region 91b into which a heating liquid flows is formed between the second end plate 94 and the second end plate 94. The first refrigerant regions 91a and the first liquid regions 91b are arranged alternately in the axial direction D1.

Each first heat exchange plate 91 and each first spacer 92 form four communication paths 901. The first end plate 93 closes each communication path 901 from the D1A side. Note that in FIG. 3, one of the four communication paths 901 is illustrated.

In addition to the first inlet 9a formed in the second end plate 94, as shown in FIG. 2, a first outlet 9b, a third inlet 9c, and a third outlet 9d are formed. ing.

Each first spacer 92 connects two of the four communication paths 901 to the first inlet 9a and the first outlet 9b, and connects the remaining two communication paths 901 to the third communication path 901. It communicates with the inlet 9c and the third outlet 9d. Thereby, the first inlet 9a and the first outlet 9b are in communication with each of the first refrigerant regions 91a. The third inlet 9c and the third outlet 9d communicate with each first liquid region 91b.

The condenser 9 is fastened to the housing 10 and the receiver case 3 in the axial direction D1 by a plurality of first fastening bolts 201 shown in FIG. Each first fastening bolt 201 is an example of a "fastening member" in the present invention.

Specifically, the receiver case 3 is placed on the D1A side of the compressor housing 13. Further, a condenser 9 is arranged on the D1A side of the receiver case 3. Then, each first fastening bolt 201 is inserted and fastened from the first end plate 93 side of the condenser 9.

Thereby, the first end plate 93, each first heat exchange plate 91, each first spacer 92, and second end plate 94 are fastened in the axial direction D1. At this time, each first fastening bolt 201 passes through the receiver case 3 in the axial direction D1 and reaches the fixed portion 133 of the compressor housing 13. In this way, the compressor housing 13, that is, the housing 10, the receiver case 3, and the condenser 9 are fastened and fixed in the axial direction D1 by each first fastening bolt 201.

In this way, by fixing the housing 10, the receiver case 3, and the condenser 9 in the axial direction D1, the condenser 9 can be connected to the D1A of the housing 10 through the receiver case 3, as shown in FIG. It is located on the D1A side in the heat pump device. Note that the number of each first fastening bolt 201 can be designed as appropriate.

Further, in the condenser 9, the seal members 921 and 922 of each first spacer 92 shown in FIG. 3 are elastically deformed by the fastening force of each first fastening bolt 201. Thereby, the space between each first heat exchange plate 91 and each first spacer 92 is sealed. Furthermore, the space between the first spacer 92 and the first end plate 93 and the space between the first spacer 92 and the second end plate 94 are similarly sealed.

Moreover, by fixing the housing 10 and the receiver case 3, as shown in FIG. 2, the D1A side of the first discharge passage 21a and the D1B side of the second discharge passage 21b are connected. The second circulation passage 22b is connected to the D1A side of the third circulation passage 22c on the side opposite to the receiver 5. Furthermore, the first heating liquid passage 33a is connected to the D1B side of the second heating liquid passage 33b on the side opposite to the heating liquid inlet 31, and the fourth heating liquid passage 33d is connected to the heating liquid outlet 32. is connected to the D1B side of the third heating liquid passage 33c on the opposite side.

Furthermore, by fixing the receiver case 3 and the condenser 9, the first inlet 9a is connected to the D1A side of the second discharge passage 21b, and the first outlet 9b is connected to the side opposite to the receiver 5. It is connected to the first circulation passage 22a. Further, the third inlet 9c is connected to the D1A side of the second heating liquid passage 33b, and the third outlet 9d is connected to the D1A side of the third heating liquid passage 33c.

As shown in FIG. 1, the evaporator 11 includes a plurality of second heat exchange plates 111, a plurality of second spacers 112, one third end plate 113, and one fourth end plate 114. It is made up of. Each second heat exchange plate 111 is also an example of a "heat exchange plate" in the present invention. Further, each second spacer 112 is also an example of a "spacer" in the present invention.

The third end plate 113 is disposed closest to the D1B side in the evaporator 11. The fourth end plate 114 is disposed closest to the D1A side in the evaporator 11. Each second heat exchange plate 111 and each second spacer 112 are arranged between the third end plate 113 and the fourth end plate 114.

Each of the second heat exchange plates 111, each of the second spacers 112, and the third and fourth end plates 113 and 114 are connected to each of the first heat exchange plates 91, each of the first spacers 92, and the first and second end plates 93 and 94, respectively. It has a symmetrical shape in the axial direction D1. Here, the space between the second heat exchange plates 111 is a second refrigerant region 111a into which a refrigerant flows or a second liquid region 111b into which a cooling liquid flows (see FIG. 2). The second refrigerant regions 111a and the second liquid regions 111b are also arranged alternately in the axial direction D1.

Further, the fourth end plate 114 is formed with a second inlet 11a, a second outlet 11b, a fourth inlet 11c, and a fourth outlet 11d. The second inlet 11a and the second outlet 11b communicate with each second refrigerant region 111a, and the fourth inlet 11c and fourth outlet 11d communicate with the second liquid region 111b.

As shown in FIG. 1, the evaporator 11 is arranged on the D1B side of the inverter housing 15. The evaporator 11 and the housing 10 are fastened together in the axial direction D1 by a plurality of second fastening bolts 203. Each second fastening bolt 203 is also an example of a "fastening member" in the present invention.

Specifically, each second fastening bolt 203 is inserted and fastened from the third end plate 113 side. Thereby, the third end plate 113, each of the second heat exchange plates 111, each of the second spacers 112, and the fourth end plate 114 are fastened in the axial direction D1. At this time, each second fastening bolt 203 reaches the inverter housing 15, so that the evaporator 11 and the housing 10 are fastened and fixed in the axial direction D1. In this way, the evaporator 11 is located closest to the D1B side in the heat pump device. Note that the number of each second fastening bolt 203 can be designed as appropriate.

By fixing the housing 10 and the evaporator 11, the second inlet 11a is connected to the D1B side of the fifth circulation passage 22e, as shown in FIG. Further, the second outlet 11b is connected to the D1B side of the first suction passage 23a. Further, the fourth inlet 11c is connected to the D1B side of the first cooling liquid passage 36a. The fourth outlet 11d is connected to the D1B side of the second cooling liquid passage 36b.

Although detailed illustrations are omitted, in the evaporator 11 as well as in the condenser 9, the space between each second heat exchange plate 111 and each second spacer 112 is sealed by the fastening force of the second fastening bolt 203. In addition, the spaces between the second spacer 112 and the third end plate 113 and between the second spacer 112 and the fourth end plate 114 are sealed.

Thus, in this heat pump device, the condenser 9, receiver case 3, housing 10, and evaporator 11 are fixed and integrated in this order from the D1A side to the D1B side. That is, in this heat pump device, the electric compressor 1 and the receiver case 3 are arranged between the condenser 9 and the evaporator 11 in the axial direction D1. Further, the receiver case 3 is arranged closer to the condenser 9 than the electric compressor 1, that is, closer to the D1A side.

Further, in this heat pump device, a discharge passage 211 is formed by the first and second discharge passages 21a and 21b, and the discharge passage 211 connects the discharge port 16b and the first inlet 9a. Further, a circulation passage 221 is formed by the first to fifth circulation passages 22a to 22e, and the first outlet 9b and the second inlet 11a are connected by the circulation passage 221. Further, a suction passage 231 is formed by the first to third suction passages 23a to 23c, and the second outlet 11b and the suction port 16a are connected by the suction passage 231. As described above, the refrigerant can flow through the first discharge passage 21a, the third circulation passage 22c, and the third suction passage 23c. That is, the refrigerant can flow through the discharge passage 211, the circulation passage 221, and the suction passage 231, respectively.

Here, the discharge passage 211 is formed in the housing 10 and the receiver case 3, and the circulation passage 221 and the suction passage 231 are formed in the housing 10. Further, the receiver 5 and the expansion valve 7 are provided in the circulation passage 221. The expansion valve 7 is located downstream of the receiver 5 in the refrigerant flow direction.

In this heat pump device configured as described above, the heating liquid flows from the heating liquid inlet 31 through the first and second heating liquid passages 33a and 33b, and from the third inlet 9c to each of the first liquids in the condenser 9. It flows into the region 91b. Similarly, the cooling liquid flows from the cooling liquid inlet 34 through the first cooling liquid passage 36a and into each second liquid region 111b of the evaporator 11 from the fourth inlet 11c.

Further, the electric motor 17 operates the compression mechanism 16 by controlling the operation of the electric motor 17 while supplying power to the electric motor 17 by the inverter circuit 18 . Thereby, the compression mechanism 16 compresses the refrigerant sucked in from the suction port 16a, and discharges the compressed refrigerant from the discharge port 16b. The high-temperature, high-pressure refrigerant discharged from the discharge port 16b passes through the discharge passage 211 and flows through each first refrigerant region 91a of the condenser 9 from the first inlet 9a.

Thereby, in the condenser 9, the refrigerant in each first refrigerant region 91a and the heating liquid in each first liquid region 91b perform heat exchange. Therefore, the heating liquid is heated to a high temperature. The heating liquid that has completed heat exchange with the refrigerant flows out of the housing 10 from the heating liquid outlet 32 via the third outlet 9d, the third and fourth heating liquid passages 33c and 33d. The heating liquid heated in the condenser 9 in this manner is used not only to heat the interior of the electric vehicle 100 but also to adjust the temperature of the battery of the electric vehicle 100 and the like.

On the other hand, the refrigerant that has completed heat exchange in the condenser 9 flows through the first circulation passage 22a from the first outlet 9b, and is separated into gas and liquid within the receiver 5. Further, the liquid phase refrigerant that has passed through the receiver 5 is depressurized by the expansion valve 7, and flows through each second refrigerant region 111a of the evaporator 11 through the second to fifth circulation passages 22b to 22e and the second inlet 11a. . At this time, the expansion valve 7 is controlled by the control device to appropriately change its opening degree. Thereby, the expansion valve 7 appropriately adjusts the pressure of the refrigerant flowing through the circulation passage 221 toward the evaporator 11 .

In the evaporator 11, the refrigerant in each second refrigerant region 111a and the cooling liquid in each second liquid region 111b exchange heat. Therefore, the cooling liquid is cooled to a low temperature. The cooling liquid that has completed heat exchange in the evaporator 11 flows out of the housing 10 from the cooling liquid outlet 35 via the fourth outlet 11d and the second cooling liquid passage 36b. The cooling liquid cooled by the evaporator 11 in this manner is used not only to cool the interior of the vehicle, but also to cool the driving motor (not shown) of the electric vehicle 100, control the temperature of the battery, and the like.

On the other hand, the refrigerant that has completed heat exchange in the evaporator 11 flows through the suction passage 231 from the second outlet 11b, and is sucked into the compression mechanism 16 from the suction port 16a. In this way, the refrigerant is compressed again in the compression mechanism 16.

In this heat pump device, both the condenser 9 and the evaporator 11 are integrated with the housing 10 in the axial direction D1 of the housing 10. Therefore, compared to a configuration in which the condenser 9 or the evaporator 11 is integrated with the housing 10 in the radial direction of the housing 10, enlargement in the radial direction is suppressed.

Further, in this heat pump device, the condenser 9, the compression mechanism 16, the electric motor 17, the inverter circuit 18, and the evaporator 11 are arranged in this order from the D1A side toward the D1B side. That is, the inverter circuit 18 is arranged between the electric motor 17 and the evaporator 11. Therefore, it is possible to make the inverter circuit 18 closer to the evaporator 11 than the electric motor 17. This allows the inverter circuit 18 to be suitably cooled by the low-temperature evaporator 11. Further, the inverter circuit 18 is further away from the condenser 9 than the electric motor 17 and the compression mechanism 16 in the axial direction D1. Therefore, the inverter circuit 18 is less affected by the heat of the condenser 9. In this respect as well, this heat pump device allows the inverter circuit 18 to be suitably cooled.

Further, since the discharge port 16b and the condenser 9 are both arranged on the D1A side of the housing 10, the discharge port 16b is arranged closer to the condenser 9 in the axial direction D1 than the suction port 16a. For this reason, for example, in the main body 131 of the compressor housing 13, the suction port 16a is provided on the D1B side and the discharge port 16b is provided on the D1A side, so that the discharge port 16b condenses more in the axial direction D1 than the suction port 16a. In this heat pump device, the discharge passage 211 can be shortened compared to a configuration in which the heat pump device is disposed far from the vessel 9.

Further, since the suction port 16a and the evaporator 11 are both arranged on the D1B side of the housing 10, the suction port 16a is arranged closer to the evaporator 11 than the discharge port 16b. Therefore, the suction passage 231 can also be shortened. These prevent the heat pump device from increasing in size as a whole.

Furthermore, in this heat pump device, the heating liquid inlet 31 and the heating liquid outlet 32 are formed in the fixed part 133 of the compressor housing 13, so that the heating liquid inlet 31 and the heating liquid outlet 32 are located near the condenser 9. It is located in Furthermore, by forming the cooling liquid inlet 34 and the cooling liquid outlet 35 in the inverter housing 15, the cooling liquid inlet 34 and the cooling liquid outlet 35 are arranged near the evaporator 11.

Therefore, in this heat pump device, the path through which the heating liquid passes from the heating liquid inlet 31 to the heating liquid outlet 32 via the condenser 9 is shortened. Similarly, the path of the cooling liquid from the cooling liquid inlet 34 to the cooling liquid outlet 35 via the evaporator 11 is also shortened. In this respect as well, this heat pump device is prevented from increasing in size as a whole.

Further, in this heat pump device, there is no need to provide the heating liquid inlet 31 and the heating liquid outlet 32 in the condenser 9, and there is no need to provide the cooling liquid inlet 34 and the cooling liquid outlet 35 in the evaporator 11. Thereby, the configurations of the condenser 9 and the evaporator 11 can be simplified, so that the enlargement of the condenser 9 and the evaporator 11 is also suppressed.

In this heat pump device, special members for providing the heating liquid inlet 31, the heating liquid outlet 32, the cooling liquid inlet 34, and the cooling liquid outlet 35 are not required. In this respect as well, this heat pump device is prevented from increasing in size.

Therefore, the heat pump device of Example 1 can suitably cool the inverter circuit 18 and has excellent mountability on the electric vehicle 100.

By the way, since both the condenser 9 and the evaporator 11 are integrated with the electric compressor 1 in the axial direction D1 of the housing 10, this heat pump device has a smaller housing 10 than the heat pump device of Patent Document 1 mentioned above. The size can be increased in the axial direction D1. However, in general, in a moving body such as the electric vehicle 100, due to the arrangement with other equipment mounted on the vehicle, the heat pump device is generally reduced in size in the radial direction of the housing 10 rather than in the axial direction D1 of the housing 10. There is a great demand for miniaturization. In other words, when securing a space for arranging the heat pump device in the electric vehicle 100, it is easier to secure the space in the axial direction D1 of the housing 10 than in the radial direction of the housing 10. Therefore, even if the heat pump device becomes larger in the axial direction D1 of the housing 10, it can be easily mounted on the electric vehicle 100.

Further, in this heat pump device, the condenser 9 includes a plurality of first heat exchange plates 91, a plurality of first spacers 92, one first end plate 93, and one second end plate 94. It is made up of. Further, the evaporator 11 is composed of a plurality of second heat exchange plates 111, a plurality of second spacers 112, one third end plate 113, and one fourth end plate 114. . For these reasons, it is possible to simplify the configurations of the condenser 9 and the evaporator 11.

Here, in the condenser 9, each first heat exchange plate 91, each first spacer 92, and first and second end plates 93 and 94 are fastened and integrated by a plurality of first fastening bolts 201. For this reason, it is possible to integrate these first heat exchange plates 91 and the like more easily than in the case of brazing. The same applies to the evaporator 11.

Furthermore, in this heat pump device, each first heat exchange plate 91, each first spacer 92, first and second end plates 93, 94, receiver case 3, and compressor housing 13 are fastened by each first fastening bolt 201. , the housing 10, the receiver case 3, and the condenser 9 can be fixed in the axial direction D1. Similarly, by fastening each second heat exchange plate 111, each second spacer 112, third and fourth end plates 113, 114, and inverter housing 15 with each second fastening bolt 203, housing 10 and evaporator 11 are connected. can be fixed in the axial direction D1.

In the condenser 9, the fastening force of each first fastening bolt 201 causes the first spacer to 92 and the first end plate 93 and between the first spacer 92 and the second end plate 94 are sealed. Therefore, leakage of refrigerant and heating liquid from the condenser 9 can be suitably prevented. The same applies to the evaporator 11.

Further, in this heat pump device, the receiver case 3 is provided between the housing 10 and the condenser 9, so that the receiver 5 is disposed between the housing 10 and the condenser 9. Thereby, while simplifying the configuration of the circulation passage 221, the refrigerant that has passed through the condenser 9 can be suitably separated into gas and liquid by the receiver 5.

Furthermore, since the electric motor 17 is disposed between the compression mechanism 16 and the evaporator 11, the electric motor 17 is disposed close to the evaporator 11. Therefore, the electric motor 17 is also easily cooled by the evaporator 11.

Further, the discharge passage 211 is formed in the housing 10 and the receiver case 3, and the circulation passage 221 and the suction passage 231 are formed in the housing 10. Thereby, none of the discharge passage 211, the circulation passage 221, and the suction passage 231 are provided outside the housing 10 and the receiver case 3 separately from the housing 10 and the receiver case 3. In this respect as well, this heat pump device has excellent mountability on the electric vehicle 100.

(Example 2)
As shown in FIG. 4, in the heat pump device of Example 2, the receiver case 3, condenser 9, housing 10, and evaporator 11 are integrated in this order from the D1A side to the D1B side. That is, the receiver case 3 is disposed closest to the D1A side, and the condenser 9 is directly fixed to the housing 10 in the axial direction D1. Further, unlike the heat pump device of the first embodiment, the second discharge passage 21b and the second and third heating liquid passages 33b and 33c are not formed in the receiver case 3.

Thereby, in this heat pump device, the first inlet 9a is connected to the D1A side of the first discharge passage 21a. In this manner, in this heat pump device, the discharge port 16b and the first inlet 9a are connected by the discharge passage 212 formed only by the first discharge passage 21a. Further, a third inlet 9c is connected to the D1A side of the first heating liquid passage 33a, and a third outlet 9d is connected to the D1A side of the fourth heating liquid passage 33d.

Further, a sixth circulation passage 22f is formed in the condenser 9, and the D1A side of the third circulation passage 22c is connected to the D1B side of the sixth circulation passage 22f. The second circulation passage 22b is connected to the D1A side of the sixth circulation passage 22f on the side opposite to the receiver 5. Thus, in this heat pump device, the circulation passage 222 is formed by the first to sixth circulation passages 22a to 22f. The other configurations of this heat pump device are the same as those of the heat pump device of Example 1, and the same components are given the same reference numerals and detailed explanations regarding the configurations will be omitted.

In this heat pump device, the receiver case 3 is disposed closest to the D1A side, so that the receiver 5 in the receiver case 3 is less likely to be affected by the heat of the compression mechanism 16 during operation.

Further, the receiver 5 is capable of suitably dissipating heat to the outside via the receiver case 3. Thereby, in this heat pump device, it is possible to suitably cool the receiver 5. Furthermore, in this heat pump device, the configuration of the discharge passage 212 is simplified, and the path through which the heating liquid passes from the heating liquid inlet 31 to the heating liquid outlet 32 via the condenser 9 is shorter. Other functions of this heat pump device are similar to those of the heat pump device of Example 1.

(Example 3)
As shown in FIG. 5, in the heat pump device of Example 3, the condenser 9, housing 10, receiver case 3, and evaporator 11 are integrated in this order from the D1A side to the D1B side. That is, the receiver case 3 is disposed between the inverter housing 15 and the evaporator 11, and the evaporator 11 is fixed to the inverter housing 15 via the receiver case 3.

Further, in this heat pump device, the condenser 9 is directly fixed to the housing 10, similar to the heat pump device of the second embodiment. Therefore, the first inlet 9a is connected to the D1A side of the first discharge passage 21a, and the discharge passage 212 is formed only by the first discharge passage 21a. Further, a third inlet 9c is connected to the D1A side of the first heating liquid passage 33a, and a third outlet 9d is connected to the D1A side of the fourth heating liquid passage 33d.

Further, in the circulation passage 221, a first outlet 9b is connected to the D1A side of the third circulation passage 22c. On the other hand, the first circulation passage 22a is connected to the D1B side of the fifth circulation passage 22e on the side opposite to the receiver 5, and the second circulation passage 22b is connected to the second inlet 11a on the side opposite to the receiver 5. Connected.

The receiver case 3 includes a third cooling liquid passage 36c, a fourth cooling liquid passage 36d, and a fourth suction liquid passage in place of the second discharge passage 21b, second and third heating liquid passages 33b and 33c. A passage 23d is formed.

The D1B side of the first cooling liquid passage 36a is connected to the D1A side of the third cooling liquid passage 36c, and the fourth inlet 11c is connected to the D1B side of the third cooling liquid passage 36c. There is. Further, the D1B side of the second cooling liquid passage 36b is connected to the D1A side of the fourth cooling liquid passage 36d, and the fourth outlet 11d is connected to the D1B side of the fourth cooling liquid passage 36d. has been done.

The D1B side of the first suction passage 23a is connected to the D1A side of the fourth suction passage 23d, and the second outlet 11b is connected to the D1B side of the fourth suction passage 23d. Thus, in this heat pump device, the suction passage 232 is formed by the first to fourth suction passages 23a to 23d. The other configuration of this heat pump device is the same as that of the heat pump device of Example 1.

In this heat pump device, the receiver case 3 is arranged between the inverter housing 15 and the evaporator 11, so that the receiver 5 in the receiver case 3 is arranged in the D1A direction with respect to the evaporator 11. Thereby, the refrigerant in the receiver 5 can be suitably cooled by the low-temperature evaporator 11. Further, in this heat pump device as well, the configuration of the discharge passage 212 is simplified, and the path through which the heating liquid reaches the heating liquid outlet 32 from the heating liquid inlet 31 via the condenser 9 is shorter. Other functions of this heat pump device are similar to those of the heat pump device of Example 1.

(Example 4)
As shown in FIG. 6, in the heat pump device of the fourth embodiment, the receiver case 3 is omitted, and the receiver 5 and the expansion valve 7 are housed in the compressor housing 13, that is, the housing 10. Thereby, in this heat pump device, the condenser 9 is directly fixed to the housing 10. Therefore, the first inlet 9a is connected to the D1A side of the first discharge passage 21a, and the discharge passage 212 is formed only by the first discharge passage 21a.

Further, in this heat pump device, while the first circulation passage 22a and the second circulation passage 22b are formed in the compressor housing 13, the third circulation passage 22c is not formed in the compressor housing 13. Therefore, the second circulation passage 22b is connected to the D1A side of the fourth circulation passage 22d on the side opposite to the receiver 5. Thereby, in this heat pump device, a circulation passage 223 is formed by the first, second, fourth, and fifth circulation passages 22a, 22b, 22d, and 22e. The other configuration of this heat pump device is the same as that of the heat pump device of Example 1. Note that the receiver 5 and the expansion valve 7 may be housed in the motor housing 14 or the inverter housing 15.

In this heat pump device, by omitting the receiver case 3, it is possible to downsize the entire heat pump device in the axial direction D1. Further, in this heat pump device as well, the configuration of the discharge passage 212 is simplified, and the path through which the heating liquid reaches the heating liquid outlet 32 from the heating liquid inlet 31 via the condenser 9 is shorter. Other functions of this heat pump device are similar to those of the heat pump device of Example 1.

(Example 5)
As shown in FIG. 7, the heat pump device of the fifth embodiment includes an accumulator case 41, an accumulator 42, and a first orifice 43 instead of the receiver case 3, receiver 5, and expansion valve 7. The first orifice 43 is an example of a "fixed aperture" in the present invention.

Further, this heat pump device includes a first pressure sensor 6a, a first temperature sensor 6b, a second pressure sensor 6c, and a second temperature sensor 6d. The first pressure sensor 6a and the first temperature sensor 6b constitute a "high pressure side detection section" in the present invention. The second pressure sensor 6c and the second temperature sensor 6d constitute a "low pressure side detection section" in the present invention.

Although detailed illustration is omitted, like the receiver case 3, the accumulator case 41 is formed in a substantially rectangular box shape. Accumulator case 41 is arranged on the D1B side with respect to inverter housing 15. That is, the accumulator case 41 is arranged in the axial direction D1 with respect to the housing 10 and, by extension, the electric compressor 1, and is located on the D1B side with respect to the electric compressor 1.

The accumulator case 41 is formed with a seventh circulation passage 22g, a fifth suction passage 23e, and a sixth suction passage 23f, as well as a fifth cooling liquid passage 36e and a sixth cooling liquid passage 36f. is formed.

Accumulator 42 is housed within accumulator case 41. The accumulator 42 is located between the fifth suction passage 23e and the sixth suction passage 23f, and is connected to the fifth suction passage 23e and the sixth suction passage 23f. The accumulator 42 is connected to a control device (not shown). Note that the accumulator 42 has the same configuration as a known accumulator, so detailed explanation will be omitted.

The first orifice 43 is formed in the accumulator case 41, and reduces the passage area of the seventh circulation passage 22g to a predetermined size. For this reason, the refrigerant is depressurized when flowing through the third circulation passage 22c. Note that the first orifice 43 may be formed in the motor housing 14, for example, to reduce the passage area of the third circulation passage 22c to a predetermined size.

In this heat pump device, the evaporator 11, the accumulator case 41, and the housing 10 are fastened and fixed in the axial direction D1 by respective second fastening bolts 203 (see FIG. 1). Further, in this heat pump device, like the heat pump devices of Examples 2 to 4, the condenser 9 is directly fixed to the housing 10 in the axial direction D1.

Thus, by fixing the evaporator 11, the accumulator case 41, and the housing 10, the D1A side of the seventh circulation passage 22g is connected to the D1B side of the fifth circulation passage 22e. Further, the D1B side of the seventh circulation passage 22g is connected to the second inlet 11a. Furthermore, the fifth suction passage 23e is connected to the second outlet 11b on the opposite side from the accumulator 42. Further, the sixth suction passage 23f is connected to the D1B side of the first suction passage 23a on the side opposite to the accumulator 42.

Thus, in this heat pump device, the discharge passage 212 is formed only in the first discharge passage 21a, and the circulation passage 224 is formed by the third, fourth, fifth, and seventh circulation passages 22c, 22d, 22e, and 22g. A suction passage 233 is formed by the first, second, third, fifth, and sixth suction passages 23a, 23b, 23c, 23e, and 23f.

Further, in this heat pump device, the first cooling liquid passage 36a is connected to the D1A side of the fifth cooling liquid passage 36e on the side opposite to the cooling liquid inlet 34, and the second cooling liquid passage 36b is connected to the D1A side of the fifth cooling liquid passage 36e. It is connected to the D1A side of the sixth cooling liquid passage 36f on the side opposite to the cooling liquid outlet 35. Further, the D1B side of the fifth cooling liquid passage 36e is connected to the fourth inlet 11c, and the D1B side of the sixth cooling liquid passage 36f is connected to the fourth outlet 11d.

The first pressure sensor 6a, the first temperature sensor 6b, the second pressure sensor 6c, and the second temperature sensor 6d are all provided within the inverter housing 15, and are each connected to the inverter circuit 18. Note that the first pressure sensor 6a, the first temperature sensor 6b, the second pressure sensor 6c, and the second temperature sensor 6d may be provided within the compressor housing 13 or the motor housing 14. Furthermore, by omitting the first temperature sensor 6b, the first pressure sensor 6a alone may constitute the "high pressure side detection section" in the present invention.

The first pressure sensor 6a is capable of detecting the pressure of the refrigerant flowing through the fifth circulation passage 22e. The first temperature sensor 6b is capable of detecting the temperature of the refrigerant flowing through the fifth circulation passage 22e. Thereby, the first pressure sensor 6a and the first temperature sensor 6b detect the pressure and temperature of the refrigerant flowing upstream of the first orifice 43 in the circulation passage 224, respectively. Note that the first pressure sensor 6a and the first temperature sensor 6b may detect the pressure and temperature of the refrigerant flowing through the third circulation passage 22c or the fourth circulation passage 22d, respectively. Further, the first pressure sensor 6a and the first temperature sensor 6b may detect the pressure and temperature of the refrigerant flowing through the seventh circulation passage 22g, respectively, as long as they are upstream of the first orifice 43.

The second pressure sensor 6c is capable of detecting the pressure of the refrigerant flowing through the first suction passage 23a. The second temperature sensor 6d is capable of detecting the temperature of the refrigerant flowing through the first suction passage 23a. Thereby, the second pressure sensor 6c and the second temperature sensor 6d respectively detect the pressure and temperature of the refrigerant flowing between the accumulator 42 and the suction port 16a in the suction passage 233. Note that the second pressure sensor 6c and the second temperature sensor 6d may detect the pressure and temperature of the refrigerant flowing through the second suction passage 23b, the third suction passage 23c, or the sixth suction passage 23f, respectively. The other configuration of this heat pump device is the same as that of the heat pump device of Example 1.

In this heat pump device, the refrigerant flowing through the circulation passage 224 toward the evaporator 11 after completing heat exchange in the condenser 9 is reduced to a predetermined pressure by the first orifice 43 when flowing through the seventh circulation passage 22g. be done. The refrigerant that has undergone heat exchange in the evaporator 11 then flows into the accumulator 42 . Thereby, the accumulator 42 separates the refrigerant into gas and liquid while accumulating pressure therein. Therefore, liquid phase refrigerant is suitably prevented from being sucked into the compression mechanism 16 through the suction port 16a. Here, by providing the accumulator case 41 between the evaporator 11 and the housing 10, the accumulator 42 in the accumulator case 41 is arranged on the D1A side of the evaporator 11. This makes it possible to simplify the configuration of the suction passage 233.

In addition, in this heat pump device, the pressure and temperature of the refrigerant flowing through the fifth circulation passage 22d, that is, the state of the refrigerant in the state before being depressurized in the first orifice 43 after completing heat exchange in the condenser 9. Pressure and temperature are detected by a first pressure sensor 6a and a first temperature sensor 6b. Furthermore, in this heat pump device, the pressure and temperature of the refrigerant flowing through the first suction passage 23a, that is, the pressure and temperature of the refrigerant in the state before reaching the suction port 16a after being pressure-accumulated in the accumulator 42 and separated into gas and liquid. Temperature is detected by a second pressure sensor 6c and a second temperature sensor 6d. Thereby, the inverter circuit 18 detects the current operation of the electric compressor 1 through the temperature and pressure of the refrigerant detected by the first pressure sensor 6a, the first temperature sensor 6b, the second pressure sensor 6c, and the second temperature sensor 6d. It is now possible to detect the status and, by extension, the operating status of the heat pump device.

Specifically, in the inverter circuit 18, if the pressure of the refrigerant detected by the first pressure sensor 6a is higher than a preset threshold, the compression mechanism 16 compresses and discharges the refrigerant at a pressure higher than the set value. It is determined that there is. As a result, in this heat pump device, the inverter circuit 18 controls the operation of the electric motor 17 to prevent the compression mechanism 16 and, by extension, the electric compressor 1 from operating when the refrigerant is at an excessively high pressure.

Further, the inverter circuit 18 measures the state of cooling of the refrigerant through heat exchange in the condenser 9, based on the temperature of the refrigerant detected by the first pressure sensor 6a. Here, if the refrigerant is not properly cooled by heat exchange, in the heat pump device, the inverter circuit 18 controls the operation of the electric motor 17 to adjust the flow rate of the refrigerant discharged from the compression mechanism 16 .

Further, the inverter circuit 18 measures the pressure accumulation of the refrigerant and the state of gas-liquid separation in the accumulator 42 through the pressure and temperature of the refrigerant detected by the second pressure sensor 6c and the second temperature sensor 6d, respectively. Here, if the pressure accumulation and gas-liquid separation of the refrigerant in the accumulator 42 are not performed appropriately, in the heat pump device, the inverter circuit 18 controls the operation of the compression mechanism 16 through the operation control of the electric motor 17. Further, in the heat pump device, the operation of the accumulator 42 is controlled. In this way, this heat pump device suitably prevents liquid phase refrigerant from being sucked into the compression mechanism 16. Other functions of this heat pump device are similar to those of the heat pump device of Example 1.

(Example 6)
As shown in FIG. 8, in the heat pump device of Example 6, the condenser 9, housing 10, evaporator 11, and accumulator case 41 are integrated in this order from the D1A side to the D1B side. In other words, the accumulator case 41 is disposed closest to the D1B side.

Unlike the heat pump device of Example 5, in this heat pump device, the seventh circulation passage 22g, the fifth cooling liquid passage 36e, and the sixth cooling liquid passage 36f are not formed in the accumulator case 41. Thereby, the second inlet 11a is connected to the D1B side of the fifth circulation passage 22e. Thus, in this heat pump device, the circulation passage 225 is formed by the third to fifth circulation passages 22c to 22e.

Further, in this heat pump device, a second orifice 44 is formed in the inverter housing 15. The second orifice 44 is also an example of a "fixed aperture" in the present invention. The second orifice 44 reduces the passage area of the fifth circulation passage 22e to a predetermined size. Therefore, the refrigerant heading toward the evaporator 11 is reduced to a predetermined pressure while flowing through the fifth circulation passage 22e.

Further, in this heat pump device, the fourth inlet 11c is connected to the D1B side of the first cooling liquid passage 36a, and the fourth outlet 11d is connected to the D1B side of the second cooling liquid passage 36b. .

In this heat pump device, a seventh suction passage 23g is formed in the evaporator 11. Thereby, the D1B side of the seventh suction passage 23g is connected to the sixth suction passage 23f on the side opposite to the accumulator 42. Further, the D1A side of the seventh suction passage 23g is connected to the D1B side of the first suction passage 23a. In this way, a suction passage 234 is formed by the first to third, fifth to seventh suction passages 23a to 23c, and 23e to 23g.

Further, unlike the heat pump device of Example 5, this heat pump device does not include a first pressure sensor 6a, a first temperature sensor 6b, a second pressure sensor 6c, and a second temperature sensor 6d. The other configuration of this heat pump device is the same as that of the heat pump device of Example 5.

In this heat pump device, the accumulator case 41 is disposed closest to the D1B side, so that the accumulator 42 inside the accumulator case 41 can suitably radiate heat to the outside via the accumulator case 41. Thereby, the refrigerant in the accumulator 42 can be appropriately cooled.

In addition, this heat pump device can simplify the configuration and reduce manufacturing costs by omitting the first pressure sensor 6a, first temperature sensor 6b, second pressure sensor 6c, and second temperature sensor 6d. It has become. Other functions of this heat pump device are similar to those of the heat pump devices of Examples 1 and 5.

(Example 7)
As shown in FIG. 9, in the heat pump device of the seventh embodiment, the accumulator case 41 is omitted, and the accumulator 42 is housed within the motor housing 14, that is, within the housing 10. Note that the accumulator 42 may be housed within the inverter housing 15 or the compressor housing 13.

Further, in this heat pump device, the second suction passage 23b is not formed in the motor housing 14, but the fifth suction passage 23e and the sixth suction passage 23f are formed. The fifth suction passage 23e is connected to the D1A side of the first suction passage 23a on the side opposite to the accumulator 42. Further, the sixth suction passage 23f is connected to the D1B side of the third suction passage 23c on the side opposite to the accumulator 42. In this way, a suction passage 235 is formed by the first, third, fifth, and sixth suction passages 23a, 23c, 23e, and 23f.

Further, like the heat pump device of the sixth embodiment, in this heat pump device as well, a circulation passage 225 is formed by the third to fifth circulation passages 22c to 22e. A third orifice 45 is formed in the motor housing 14. The third orifice 45 is also an example of a "fixed aperture" in the present invention. The third orifice 45 reduces the passage area of the fourth circulation passage 22d to a predetermined size. Therefore, the refrigerant is reduced in pressure to a predetermined pressure when flowing through the fourth circulation passage 22d.

Furthermore, like the heat pump device of Example 1, in this heat pump device as well, the fourth inlet 11c is connected to the D1B side of the first cooling liquid passage 36a, and the fourth outlet 11d is connected to the second cooling liquid passage 36a. It is connected to the D1B side of 36b. Furthermore, this heat pump device also does not include the first pressure sensor 6a, the first temperature sensor 6b, the second pressure sensor 6c, and the second temperature sensor 6d. The other configuration of this heat pump device is the same as that of the heat pump device of Example 5.

In this heat pump device, by omitting the accumulator case 41, it is possible to downsize the entire heat pump device in the axial direction D1. Also, in this heat pump device, by omitting the first pressure sensor 6a, first temperature sensor 6b, second pressure sensor 6c, and second temperature sensor 6d, it is possible to simplify the configuration and reduce manufacturing costs. It has become. Other functions of this heat pump device are similar to those of the heat pump devices of Examples 1 and 5.

(Example 8)
As shown in FIG. 10, the heat pump device of Example 8 includes a condenser 90 instead of the condenser 9. Further, this heat pump device does not include the receiver case 3 and the receiver 5. As a result, in this heat pump device, the discharge passage 212 is formed only by the first discharge passage 21a, the circulation passage 225 is formed by the third to fifth circulation passages 22c to 22e, and the first to third suction passages 23a are formed. A suction passage 231 is formed by 23c.

Furthermore, this heat pump device includes a third pressure sensor 8a, a third temperature sensor 8b, a fourth pressure sensor 8c, and a fourth temperature sensor 8d. The third pressure sensor 8a and the third temperature sensor 8b constitute a "circulation passage side detection section" in the present invention. The fourth pressure sensor 8c and the fourth temperature sensor 8d constitute the "suction passage side detection section" in the present invention.

Although detailed illustrations are omitted, like the condenser 9, the condenser 90 also includes a plurality of first heat exchange plates 91, a plurality of first spacers 92, one first end plate 93, It is composed of one second end plate 94. Regarding the condenser 90, the first end plate 93, each first heat exchange plate 91, each first spacer 92, and second end plate 94 are fastened in the axial direction D1 by each first fastening bolt 201, It is fixed to the housing 10 by each first fastening bolt 201. Thus, in this heat pump device, the condenser 90 is integrated with the housing 10 in the axial direction D1 of the housing 10, and the condenser 90 is arranged on the D1A side of the housing 10.

The condenser 90 has a first inlet 90a, a first outlet 90b, a third inlet 90c, and a third outlet 90d. It has a refrigerant region 90f and a first liquid region 90g. Furthermore, the condenser 90 has a receiver 90h. The receiver 90h is an example of a "condenser side gas-liquid separation section" in the present invention.

As described above, by fixing the condenser 90 to the housing 10, the first inlet 90a is connected to the D1A side of the first discharge passage 21a. Further, the first outlet 90b is connected to the D1A side of the third circulation passage 22c. Further, the third inlet 90c is connected to the D1A side of the first heating liquid passage 33a. The third outlet 90d is connected to the D1A side of the fourth heating liquid passage 33d.

The first condenser-side refrigerant region 90e and the second condenser-side refrigerant region 90f are located between the first inlet 90a and the first outlet 90b in the flow direction of the refrigerant in the condenser 90. The first refrigerant region 90e on the condenser side is connected to the first inlet 90a on the opposite side to the first discharge passage 21a at the most upstream side in the flow direction of the refrigerant. The condenser-side second refrigerant region 90f is located downstream of the condenser-side first refrigerant region 90e in the refrigerant flow direction. The condenser-side second refrigerant region 90f is connected to the first outlet 90b at the most downstream side in the refrigerant flow direction on the opposite side to the third circulation passage 22c.

Further, the first refrigerant region 90e on the condenser side is connected to the receiver 90h at its most downstream side in the flow direction of the refrigerant. The condenser-side second refrigerant region 90f is connected to the receiver 90h at its most upstream side in the refrigerant flow direction. Thereby, the receiver 90h is located between the condenser side first refrigerant area 90e and the condenser side second refrigerant area 90f in the flow direction of the refrigerant in the condenser 90, and the receiver 90h is located between the condenser side first refrigerant area 90e and the condenser side second refrigerant area 90f. 90e and the condenser side second refrigerant region 90f are connected. Then, the receiver 90h causes the refrigerant that has passed through the condenser-side first refrigerant region 90e to flow into the condenser-side second refrigerant region 90f in a gas-liquid separated state.

The first liquid region 90g is connected to the third inlet 90c on the opposite side from the first heating liquid passage 33a at its most upstream side in the direction of flow of the heating liquid. Further, the first liquid region 90g is connected to the third outlet 90d at the most downstream side in the direction of flow of the heating liquid on the opposite side to the fourth heating liquid passage 33d.

Further, in this heat pump device, the expansion valve 7 is provided in the fifth circulation passage 22e. Thereby, the expansion valve 7 is disposed within the inverter housing 15. Note that the expansion valve 7 may be provided in the third circulation passage 22c or the fourth circulation passage 22d.

The third pressure sensor 8a, the third temperature sensor 8b, the fourth pressure sensor 8c, and the fourth temperature sensor 8d are all provided within the inverter housing 15, and are each connected to the inverter circuit 18. Note that the third pressure sensor 8a, the third temperature sensor 8b, the fourth pressure sensor 8c, and the fourth temperature sensor 8d may be provided within the compressor housing 13 or the motor housing 14. Furthermore, by omitting the third temperature sensor 8b, the third pressure sensor 8a alone may constitute the "circulation passage side detection section" in the present invention.

The third pressure sensor 8a is capable of detecting the pressure of the refrigerant flowing upstream of the expansion valve 7 in the fifth circulation passage 22e. The third temperature sensor 8b is capable of detecting the temperature of the refrigerant flowing upstream of the expansion valve 7 in the fifth circulation passage 22e. That is, the third pressure sensor 8a and the third temperature sensor 8b can respectively detect the pressure and temperature of the refrigerant in the state after the heat exchange in the condenser 90 and before the pressure is reduced by the expansion valve 7. ing. Note that the third pressure sensor 8a and the third temperature sensor 8b may detect the pressure and temperature of the refrigerant flowing through the third circulation passage 22c or the fourth circulation passage 22d, respectively. Furthermore, as described above, when the expansion valve 7 is provided in the third circulation passage 22c or the fourth circulation passage 22d, the third pressure sensor 8a and the third temperature sensor 8b are located at the position where the expansion valve 7 is provided. Correspondingly, the pressure and temperature of the refrigerant flowing upstream of the expansion valve 7 in the circulation passage 225 are detected.

The fourth pressure sensor 8c is capable of detecting the pressure of the refrigerant flowing through the first suction passage 23a. The fourth temperature sensor 8d is capable of detecting the temperature of the refrigerant flowing through the first suction passage 23a. In this way, the fourth pressure sensor 8c and the fourth temperature sensor 8d measure the pressure and temperature of the refrigerant flowing through the suction passage 231, that is, the state after completing heat exchange in the evaporator 11 and before reaching the suction port 16a. It is possible to detect the pressure and temperature of a certain refrigerant. Note that the fourth pressure sensor 8c and the fourth temperature sensor 8d measure the pressure of the refrigerant flowing through the suction passage 231 by detecting the pressure and temperature of the refrigerant flowing through the second suction passage 23b or the third suction passage 23c, respectively. and temperature may be detected respectively.

The pressure and temperature of the refrigerant detected by the third pressure sensor 8a, third temperature sensor 8b, fourth pressure sensor 8c, and fourth temperature sensor 8d are transmitted to the inverter circuit 18. The other configuration of this heat pump device is the same as that of the heat pump device of Example 1.

In this heat pump device, high-temperature, high-pressure refrigerant compressed by the compression mechanism 16 flows into the condenser 90 from the first inlet 90a via the discharge port 16b and the discharge passage 212. This refrigerant then flows through the first refrigerant region 90e on the condenser side. Further, the heating liquid flows from the heating liquid inlet 31 through the first heating liquid passage 33a, flows into the condenser 90 from the third inlet 90c, and flows in the first liquid region 90g.

As a result, in the condenser 90, the refrigerant flowing in the first condenser-side refrigerant region 90e and the heating liquid flowing in the first liquid region 90g exchange heat. In this way, the heating liquid is heated. The refrigerant that has passed through the first refrigerant region 90e on the condenser side flows through the second refrigerant region 90f on the condenser side in a gas-liquid separated state by the receiver 90h. In other words, the refrigerant flowing within the second refrigerant region 90f on the condenser side is almost in a liquid phase.

The refrigerant flowing in the second refrigerant region 90f on the condenser side also heats the heating liquid by exchanging heat with the heating liquid flowing in the first liquid region 90g. More specifically, the refrigerant flowing in the second refrigerant region 90f on the condenser side exchanges heat with the heating liquid before being heated by the refrigerant flowing in the first refrigerant region 90e on the condenser side. Further, the refrigerant flowing in the second refrigerant region 90f on the condenser side is supercooled by radiating heat to the heating liquid. The refrigerant thus supercooled flows out from the first outlet 90b and flows through the circulation passage 225 toward the expansion valve 7. The heating liquid heated by heat exchange flows out of the housing 10 through the third outlet 90d, the fourth heating liquid passage 33d, and the heating liquid outlet 32.

Thus, in this heat pump device, the refrigerant after being separated into gas and liquid by the receiver 90h flows through the second refrigerant region 90f on the condenser side. Therefore, the refrigerant flowing in the second refrigerant region 90f on the condenser side can be suitably supercooled by heat exchange with the heating liquid flowing in the first liquid region 90g. Thereby, the refrigerant flowing through the circulation passage 225 toward the expansion valve 7, that is, the refrigerant before being depressurized by the expansion valve 7, can be turned into a liquid phase with high reliability. As a result, in this heat pump device, the generation of gas phase refrigerant at the second inlet 11a of the evaporator 11 can be suitably suppressed, so that the cooling liquid can be suitably cooled by heat exchange in the evaporator 11. It is now possible.

Further, in this heat pump device, the pressure and temperature of the refrigerant in the state before being depressurized by the expansion valve 7 after completing heat exchange in the condenser 90 are detected by the third pressure sensor 8a and the third temperature sensor 8b. be done. Furthermore, after the heat exchange in the evaporator 11 is completed, the pressure and temperature of the refrigerant in the state before reaching the suction port 16a are detected by the fourth pressure sensor 8c and the fourth temperature sensor 8d. Thereby, the inverter circuit 18 determines the current operation of the electric compressor 1 through the temperature and pressure of the refrigerant detected by the third pressure sensor 8a, the third temperature sensor 8b, the fourth pressure sensor 8c, and the fourth temperature sensor 8d. It is now possible to detect the status and, by extension, the operating status of the heat pump device.

Specifically, in the inverter circuit 18, if the pressure of the refrigerant detected by the third pressure sensor 8a is higher than a preset threshold, the compression mechanism 16 compresses and discharges the refrigerant at a pressure higher than the set value. It is determined that there is. As a result, in this heat pump device, the inverter circuit 18 controls the operation of the electric motor 17 to prevent the compression mechanism 16 and, by extension, the electric compressor 1 from operating when the refrigerant is at an excessively high pressure.

Further, the inverter circuit 18 measures the state of supercooling of the refrigerant in the second refrigerant region 90f on the condenser side of the condenser 90 based on the temperature of the refrigerant detected by the third pressure sensor 8a. Here, if the refrigerant is not properly subcooled, in the heat pump device, the inverter circuit 18 controls the operation of the electric motor 17 to adjust the flow rate of the refrigerant discharged from the compression mechanism 16 . Further, the heat pump device adjusts the opening degree of the expansion valve 7 based on the pressure and temperature of the refrigerant detected by the third pressure sensor 8a and the third temperature sensor 8b, respectively. Furthermore, this heat pump device is also capable of detecting an abnormality in the expansion valve 7 based on the state of supercooling of the refrigerant.

In addition, the inverter circuit 18 determines the heating state of the refrigerant that has completed heat exchange in the evaporator 11 through the pressure and temperature of the refrigerant in the suction passage 231 detected by the fourth pressure sensor 8c and the fourth temperature sensor 8d, respectively. In other words, super heat is measured. Here, if the refrigerant is not properly superheated, in the heat pump device, in addition to adjusting the opening degree of the expansion valve 7, the inverter circuit 18 controls the operation of the compression mechanism 16 by controlling the operation of the electric motor 17. . In this way, this heat pump device suitably prevents liquid phase refrigerant from being sucked into the compression mechanism 16. Other functions of this heat pump device are similar to those of the heat pump device of Example 1.

(Example 9)
As shown in FIG. 11, the heat pump device of Example 9 includes an evaporator 115 instead of the evaporator 11. Further, this heat pump device also does not include the receiver case 3, the receiver 5, and the expansion valve 7. As a result, in this heat pump device, the discharge passage 212 is formed only by the first discharge passage 21a, the circulation passage 225 is formed by the third to fifth circulation passages 22c to 22e, and the first to third suction passages 23a are formed. A suction passage 231 is formed by 23c.

Further, in this heat pump device, the condenser 9 is fixed to the housing 10, and the condenser 9 is located on the D1A side of the housing 10. In the condenser 9, the D1A side of the first discharge passage 21a is connected to the first inlet 9a, and the D1A side of the third circulation passage 22c is connected to the first outlet 9b. Further, the D1A side of the first heating liquid passage 33a is connected to the third inlet 9c, and the D1A side of the fourth heating liquid passage 33d is connected to the third outlet 9d.

Although detailed illustrations are omitted, similarly to the evaporator 11, the evaporator 115 includes a plurality of second heat exchange plates 111, a plurality of second spacers 112, and one third end plate 113. It is composed of one fourth end plate 114. Regarding the evaporator 115 as well, while the third end plate 113, each second heat exchange plate 111, each second spacer 112, and fourth end plate 114 are fastened in the axial direction D1 by each second fastening bolt 203, It is fixed to the inverter housing 15 and eventually to the housing 10 by each second fastening bolt 203 . Thus, in this heat pump device, the evaporator 115 is integrated with the housing 10 in the axial direction D1 of the housing 10, and the evaporator 115 is arranged on the D1B side of the housing 10.

The evaporator 115 has a second inlet 115a, a second outlet 115b, a fourth inlet 115c, and a fourth outlet 115d. Further, the evaporator 115 includes an evaporator-side first refrigerant region 115e, an evaporator-side second refrigerant region 115f, a second liquid region 115g, a receiver 115h, and an expansion valve 115i. The receiver 115h is an example of the "evaporator side gas-liquid separation section" in the present invention. Furthermore, the expansion valve 115i is an example of the "evaporator-side throttle section" in the present invention.

As described above, by fixing the evaporator 115 to the housing 10, the second inlet 115a is connected to the D1B side of the fifth circulation passage 22e. Further, the second outlet 115b is connected to the D1B side of the first suction passage 23a. Further, the fourth inlet 115c is connected to the D1B side of the first cooling liquid passage 36a. The fourth outlet 115d is connected to the D1B side of the second cooling liquid passage 36b.

The evaporator-side first refrigerant region 115e and the evaporator-side second refrigerant region 115f are located between the second inlet 115a and the second outlet 115b in the flow direction of the refrigerant in the evaporator 115. Further, the evaporator-side second refrigerant region 115f is located downstream of the evaporator-side first refrigerant region 115e in the flow direction of the refrigerant in the evaporator 115. The evaporator-side second refrigerant region 115f is connected to the evaporator-side first refrigerant region 115e at its most upstream side in the refrigerant flow direction. Further, in the evaporator-side second refrigerant region 115f, the most downstream side in the refrigerant flow direction thereof is connected to the second outlet 115b on the opposite side to the first suction passage 23a.

The receiver 115h is located between the second inlet 115a and the evaporator-side first refrigerant region 115e in the refrigerant flow direction in the evaporator 115, and is located between the second inlet 115a and the evaporator-side first refrigerant region 115e. That is, the receiver 115h is located downstream of the second inlet 115a and upstream of the evaporator-side first refrigerant region 115e in the flow direction of the refrigerant in the evaporator 115. The receiver 115h allows the refrigerant flowing from the second inlet 115a to flow into the evaporator-side first refrigerant region 115e in a gas-liquid separated state.

The expansion valve 115i is arranged between the evaporator-side first refrigerant region 115e and the evaporator-side second refrigerant region 115f. Like the expansion valve 7, the expansion valve 115i is also connected to a control device (not shown).

The second liquid region 115g is connected to the fourth inlet 115c on the opposite side to the first cooling liquid passage 36a at its most upstream side in the direction of flow of the cooling liquid. Further, the second liquid region 115g is connected to the fourth outlet 115d on the opposite side to the second cooling liquid passage 36b at its most downstream side in the direction of flow of the cooling liquid. The other configuration of this heat pump device is the same as that of the heat pump device of Example 1.

In this heat pump device, the cooling liquid flows from the cooling liquid inlet 34 through the first cooling liquid passage 36a, flows into the evaporator 115 from the fourth inlet 115c, and flows through the second liquid region 115g. Further, the refrigerant that has passed through the condenser 9 and the circulation passage 225 flows into the evaporator 115 from the second inlet 115a. The refrigerant that has flowed into the evaporator 115 in this way is first separated into gas and liquid by the receiver 115h. Therefore, the refrigerant flowing in the evaporator-side first refrigerant region 115e is substantially in a liquid phase.

The refrigerant flowing in the evaporator-side first refrigerant region 115e exchanges heat with the cooling liquid flowing in the second liquid region 115g. Thereby, the refrigerant flowing in the evaporator-side first refrigerant region 115e is supercooled. The refrigerant thus supercooled is depressurized by the expansion valve 115i and flows through the evaporator-side second refrigerant region 115f. At this time, the expansion valve 115i is controlled by the control device to appropriately change its opening degree. Thereby, the expansion valve 115i appropriately adjusts the pressure of the refrigerant flowing in the evaporator-side second refrigerant region 115f.

Thus, in the evaporator 115, the cooling liquid is cooled by heat exchange between the refrigerant flowing in the evaporator-side second refrigerant region 115f and the cooling liquid flowing in the second liquid region 115g. More specifically, the refrigerant flowing in the second evaporator refrigerant region 115f exchanges heat with the cooling liquid that has completed heat exchange with the refrigerant flowing in the first evaporator refrigerant region 115e. After completing the heat exchange with the cooling liquid, the refrigerant flows out from the second outlet 115b and is sucked into the compression mechanism 16 through the suction passage 231. On the other hand, the cooling liquid cooled by heat exchange with the refrigerant flows out of the housing 10 through the fourth outlet 115d, the second cooling liquid passage 36b, and the cooling liquid outlet 35.

In this manner, in this heat pump device, the refrigerant flowing from the second inlet 115a is separated into gas and liquid by the receiver 115h, and then flows through the first refrigerant region 115e on the evaporator side. Therefore, by heat exchange with the cooling liquid, it is possible to suitably supercool the refrigerant flowing in the evaporator-side first refrigerant region 115e. Thereby, the refrigerant that has passed through the evaporator side first refrigerant region 115e, that is, the refrigerant before being depressurized by the expansion valve 115i, can be turned into a liquid phase with high reliability. As a result, in this heat pump device, the pressure of the refrigerant can be suitably reduced in the expansion valve 115i. Therefore, the cooling liquid can be suitably cooled by heat exchange between the refrigerant flowing in the second refrigerant region 115f on the evaporator side and the cooling liquid flowing in the second liquid region 115g. There is. Other functions of this heat pump device are similar to those of the heat pump device of Example 1.

(Example 10)
As shown in FIG. 12, the heat pump device according to the tenth embodiment includes an evaporator 116 in place of the evaporator 115 in the heat pump device according to the ninth embodiment. Similarly to the evaporators 11 and 115, this evaporator 116 is also configured by a plurality of second heat exchange plates 111, etc., and is fixed to the housing 10 by each second fastening bolt 203. placed on the side.

The evaporator 116 has a second inlet 116a, a second outlet 116b, a fourth inlet 116c, and a fourth outlet 116d. The evaporator 116 also includes an evaporator-side first refrigerant region 116e, an evaporator-side second refrigerant region 116f, an evaporator-side third refrigerant region 116g, a second liquid region 116h, a receiver 116i, and an expansion valve 116j. It has The receiver 116i is also an example of the "evaporator side gas-liquid separation section" in the present invention. Further, the expansion valve 116j is also an example of the "evaporator-side throttle section" in the present invention.

The second inlet 116a is connected to the D1B side of the fifth circulation passage 22e. Further, the second outlet 116b is connected to the D1B side of the first suction passage 23a. Further, the fourth inlet 116c is connected to the D1B side of the first cooling liquid passage 36a. The fourth outlet 116d is connected to the D1B side of the second cooling liquid passage 36b.

The evaporator-side first refrigerant region 116e, the evaporator-side second refrigerant region 116f, and the evaporator-side third refrigerant region 116g have a second inlet 116a and a second outlet 116b in the flow direction of the refrigerant in the evaporator 116. It is located between. Further, the evaporator-side second refrigerant region 116f is located downstream of the evaporator-side first refrigerant region 116e in the flow direction of the refrigerant in the evaporator 116. The evaporator-side third refrigerant region 116g is located downstream of the evaporator-side second refrigerant region 116f in the flow direction of the refrigerant in the evaporator 116. In other words, the evaporator-side third refrigerant region 116g is located furthest downstream in the refrigerant flow direction among the evaporator-side first refrigerant region 116e, the evaporator-side second refrigerant region 116f, and the evaporator-side third refrigerant region 116g. positioned.

The evaporator-side second refrigerant region 116f is connected to the evaporator-side first refrigerant region 116e at its most upstream side in the refrigerant flow direction. Further, the evaporator-side second refrigerant region 116f is connected to the evaporator-side third refrigerant region 116g at its most downstream side in the refrigerant flow direction. The evaporator-side third refrigerant region 116g is connected to the second outlet 116b on the opposite side to the first suction passage 23a at its most downstream side in the refrigerant flow direction.

The receiver 116i is located between the second inlet 116a and the evaporator-side first refrigerant region 116e in the refrigerant flow direction in the evaporator 116, and is located between the second inlet 116a and the evaporator-side first refrigerant region 116e. That is, the receiver 116i is located downstream of the second inlet 116a and upstream of the evaporator-side first refrigerant region 116e in the flow direction of the refrigerant in the evaporator 116. The receiver 116i allows the refrigerant flowing from the second inlet 116a to flow into the evaporator-side first refrigerant region 116e in a gas-liquid separated state.

The expansion valve 116j is arranged between the evaporator-side first refrigerant region 116e and the evaporator-side second refrigerant region 116f. Like the expansion valves 7 and 115i, the expansion valve 116j is also connected to a control device (not shown).

The second liquid region 116h has its most upstream side in the direction of flow of the cooling liquid connected to the fourth inlet 116c on the side opposite to the first cooling liquid passage 36a. Further, the second liquid region 116h is connected to the fourth outlet 116d on the opposite side to the second cooling liquid passage 36b at its most downstream side in the direction of flow of the cooling liquid. The other configuration of this heat pump device is the same as that of the heat pump device of Example 9.

In this heat pump device, the cooling liquid flows from the cooling liquid inlet 34 through the first cooling liquid passage 36a, flows into the evaporator 116 from the fourth inlet 116c, and flows in the second liquid region 116h. Further, the refrigerant that has passed through the condenser 9 and the circulation passage 225 flows into the evaporator 116 from the second inlet 116a. The refrigerant that has thus flowed into the evaporator 116 is first separated into gas and liquid by the receiver 116i. Therefore, the refrigerant flowing in the first refrigerant region 116e on the evaporator side is almost in a liquid phase.

The refrigerant flowing through the first evaporator refrigerant region 116e exchanges heat with the refrigerant flowing through the third evaporator refrigerant region 116g. Here, the evaporator-side third refrigerant region 116g is located downstream of the evaporator-side second refrigerant region 116f and the expansion valve 116j in the flow direction of the refrigerant. In the evaporator-side third refrigerant region 116g, the refrigerant that has passed through the evaporator-side second refrigerant region 116f, that is, the refrigerant whose pressure has been reduced by the expansion valve 116j, flows. Therefore, the refrigerant flowing in the evaporator-side first refrigerant region 116e is supercooled by heat exchange with the refrigerant flowing in the evaporator-side third refrigerant region 116g. The refrigerant thus supercooled is depressurized by the expansion valve 116j and flows through the evaporator-side second refrigerant region 116f. Note that the expansion valve 116j is also controlled by the control device to appropriately change its opening degree. Thereby, the expansion valve 116j appropriately adjusts the pressure of the refrigerant flowing in the evaporator-side second refrigerant region 116f.

The refrigerant flowing in the second evaporator-side refrigerant region 116f exchanges heat with the cooling liquid flowing in the second liquid region 116h, thereby cooling the cooling liquid. In this way, in this evaporator 116, only the refrigerant flowing in the evaporator-side second refrigerant region 116f exchanges heat with the cooling liquid. The refrigerant that has passed through the second evaporator refrigerant region 116f flows through the third evaporator refrigerant region 116g as described above. The refrigerant that has passed through the evaporator-side third refrigerant region 116g flows out from the second outlet 116b and is finally sucked into the compression mechanism 16. On the other hand, the cooling liquid cooled by heat exchange with the refrigerant flows out of the housing 10 through the fourth outlet 116d, the second cooling liquid passage 36b, and the cooling liquid outlet 35.

In this manner, in this heat pump device, the refrigerant flowing from the second inlet 116a is separated into gas and liquid by the receiver 116i, and then flows through the first refrigerant region 116e on the evaporator side. Therefore, the refrigerant flowing through the first evaporator refrigerant region 116e can be suitably supercooled by heat exchange with the refrigerant flowing through the third evaporator refrigerant region 116g. Thereby, like the heat pump device of Example 9, in this heat pump device as well, it is possible to reliably turn the refrigerant into a liquid phase before being depressurized by the expansion valve 116j. As a result, this heat pump device can also suitably reduce the pressure of the refrigerant at the expansion valve 116j. Therefore, the cooling liquid can be suitably cooled by heat exchange between the refrigerant flowing in the evaporator side second refrigerant region 116f and the cooling liquid flowing in the second liquid region 116h. There is. Other functions of this heat pump device are similar to those of the heat pump device of Example 1.

In the above, the present invention has been explained based on Examples 1 to 10, but the present invention is not limited to Examples 1 to 10, and can be applied with appropriate changes without departing from the spirit thereof. Needless to say.

For example, in the heat pump devices of Examples 1 to 10, the condensers 9 and 90 include a plurality of first heat exchange plates 91, a plurality of first spacers 92, one first end plate 93, and one and a second end plate 94. However, the present invention is not limited to this, and the condensers 9 and 90 may have other configurations. The same applies to the evaporators 11, 115, and 116.

Further, in the heat pump devices of Examples 1 to 10, the heating liquid inlet 31 and the heating liquid outlet 32 may be formed in the condensers 9 and 90.

Furthermore, in the heat pump devices of Examples 1 to 10, the heating liquid inlet 31 may be formed in the fixed part 133, the heating liquid outlet 32 may be formed in the condensers 9 and 90, and the heating liquid inlet 31 may be formed in the fixed part 133. An outlet 32 may be formed, and a heating liquid inlet 31 may be formed in the condenser 9,90.

Furthermore, in the heat pump devices of Examples 1 to 10, the cooling liquid inlet 34 and the cooling liquid outlet 35 may be formed in the evaporators 11, 115, and 116.

Furthermore, in the heat pump devices of Examples 1 to 10, the inverter housing 15 may be provided with a cooling liquid inlet 34, and the evaporators 11, 115, and 116 may be provided with cooling liquid outlets 35. A cooling liquid inlet 34 may be formed in the evaporator 11 , 115 , 116 .

Further, in the heat pump devices of Examples 1 and 2, the heating liquid inlet 31 and the heating liquid outlet 32 may be formed in the receiver case 3. Further, in the heat pump devices of the first and second embodiments, the heating liquid inlet 31 may be formed in the receiver case 3 and the heating liquid outlet 32 may be formed in the condenser 9. , and a heating liquid inlet 31 may be formed in the condenser 9.

Further, in the heat pump device of the third embodiment, a cooling liquid inlet 34 and a cooling liquid outlet 35 may be formed in the receiver case 3. Further, in the heat pump device of the third embodiment, the cooling liquid inlet 34 may be formed in the receiver case 3, the cooling liquid outlet 35 may be formed in the evaporator 11, and the cooling liquid outlet 35 may be formed in the receiver case 3. However, a cooling liquid inlet 34 may be formed in the evaporator 11.

Further, in the heat pump devices of Examples 5 and 6, the cooling liquid inlet 34 and the cooling liquid outlet 35 may be formed in the accumulator case 41. Furthermore, in the heat pump devices of Examples 5 and 6, the cooling liquid inlet 34 may be formed in the accumulator case 41 and the cooling liquid outlet 35 may be formed in the evaporator 11, and the cooling liquid outlet 35 may be formed in the accumulator case 41. , and a cooling liquid inlet 34 may be formed in the evaporator 11.

Further, the heat pump devices of Examples 1 to 4 may also be provided with a third pressure sensor 8a, a third temperature sensor 8b, a fourth pressure sensor 8c, and a fourth temperature sensor 8d, similarly to the heat pump device of Example 8. .

In addition, in the heat pump device of Example 11, the pressure and temperature of the refrigerant before reaching the expansion valve 115i via the evaporator side first refrigerant region 115e are detected by the third pressure sensor 8a and the third temperature sensor 8b, and the suction The pressure and temperature of the refrigerant flowing through the passage 231 may be detected by the fourth pressure sensor 8c and the fourth temperature sensor 8d. The same applies to the heat pump device of Example 12.

Further, in the heat pump devices of Examples 8 to 10, an accumulator 42 may be provided in the suction passage 231.

Further, in the heat pump devices of Examples 1 to 4 and 8, the expansion valve 7 is the "throttling part" in the present invention. However, the present invention is not limited to this, and a fixed throttle such as an orifice may be used as the "throttle part" in the present invention.

Further, in the heat pump apparatuses of Examples 9 and 10, the expansion valves 115i and 116j are used as "evaporator-side throttle parts" in the present invention. However, the present invention is not limited to this, and a fixed throttle such as an orifice may be used as the "evaporator side throttle section" in the present invention.

Further, the heat pump devices of Examples 6 and 7 may also include a first pressure sensor 6a, a first temperature sensor 6b, a second pressure sensor 6c, and a second temperature sensor 6d, similar to the heat pump device of Example 5. .

Furthermore, in the heat pump devices of Examples 1 to 10, the compression mechanism 16 may be arranged between the inverter circuit 18 and the electric motor 17.

Further, the heat pump devices of Examples 1 to 10 are installed in an electric vehicle 100 as a "mobile object" in the present invention. However, the "mobile object" in the present invention is not limited to this, and may be, for example, a transportation vehicle, an industrial vehicle, a ship, an aircraft, or the like.

Further, in the heat pump devices of Examples 1 to 10, at least one of the condensers 9, 90 and the evaporators 11, 115, 116 is integrated with the electric compressor 1 in the radial direction of the housing 10 perpendicular to the axial direction D1. Also good.

Furthermore, this specification includes the following inventions.
(Additional note 1)
a housing; a suction port provided in the housing for sucking refrigerant; a discharge port provided in the housing for discharging refrigerant; and a discharge port provided in the housing for sucking refrigerant from the suction port. an electric compressor having a compression mechanism for discharging, and an electric motor provided in the housing for operating the compression mechanism;
a condenser that exchanges heat between the refrigerant and the heating liquid;
Equipped with an evaporator that exchanges heat between the refrigerant and the cooling liquid,
The condenser has a first inlet that allows the refrigerant discharged from the outlet to flow in, and a first outlet that allows the refrigerant to flow out toward the evaporator.
The evaporator is a heat pump device for a mobile body, which has a second inlet into which the refrigerant flowing out from the first outflow port flows, and a second outflow port into which the refrigerant flows out toward the suction port. hand,
The electric compressor is disposed between the condenser and the evaporator, and the condenser, the electric compressor, and the evaporator are integrated,
The electric compressor further includes an inverter circuit provided in the housing and controlling the electric motor,
the inverter circuit is arranged between the compression mechanism and the evaporator,
The discharge port is located closer to the condenser than the suction port,
A heat pump device for a mobile object, wherein the suction port is located closer to the evaporator than the discharge port.
(Additional note 2)
The first outflow port and the second inflow port are connected by a circulation passage,
The heat pump device for a moving body according to supplementary note 1, wherein the circulation passage is at least partially formed in the housing.
(Additional note 3)
The circulation passage is provided with a gas-liquid separator and a constriction part located downstream of the gas-liquid separator in the refrigerant circulation direction to reduce the pressure of the refrigerant flowing through the circulation passage,
The heat pump device for a mobile body according to supplementary note 2, wherein the gas-liquid separator is disposed between the housing and the condenser.
(Additional note 4)
The circulation passage is provided with a gas-liquid separator and a constriction part located downstream of the gas-liquid separator in the refrigerant circulation direction to reduce the pressure of the refrigerant flowing through the circulation passage,
The heat pump device for a mobile body according to appendix 2, wherein the condenser is disposed between the gas-liquid separator and the electric compressor.
(Appendix 5)
The circulation passage is provided with a gas-liquid separator and a constriction part located downstream of the gas-liquid separator in the refrigerant circulation direction to reduce the pressure of the refrigerant flowing through the circulation passage,
The heat pump device for a mobile object according to supplementary note 2, wherein the gas-liquid separator is disposed between the housing and the evaporator.
(Appendix 6)
The circulation passage is provided with a gas-liquid separator and a constriction part located downstream of the gas-liquid separator in the refrigerant circulation direction to reduce the pressure of the refrigerant flowing through the circulation passage,
The heat pump device for a mobile body according to supplementary note 2, wherein the gas-liquid separator is disposed within the housing.
(Appendix 7)
The condenser includes a first refrigerant region on the condenser side connected to the first inlet;
a condenser-side second refrigerant region located downstream of the condenser-side first refrigerant region in the flow direction of the refrigerant and connected to the first outlet;
a condenser-side air outlet located between the condenser-side first refrigerant region and the condenser-side second refrigerant region and connected to the condenser-side first refrigerant region and the condenser-side second refrigerant region; It has a liquid separation part,
The refrigerant flowing through the first refrigerant region on the condenser side and the refrigerant flowing through the second refrigerant region on the condenser side exchange heat with the heating liquid,
The heat pump device for a mobile body according to appendix 2, wherein the circulation passage is provided with a constriction portion that reduces the pressure of the refrigerant flowing through the circulation passage.
(Appendix 8)
The suction port and the second outlet are connected by a suction passage,
The circulation passage is provided with a constriction part that reduces the pressure of the refrigerant flowing through the circulation passage,
a circulation path side detection section that is provided in the housing and connected to the inverter circuit, and that detects the pressure of refrigerant flowing upstream of the constriction section in the circulation path;
Supplementary Notes 2 to 7, further comprising a suction passage-side detection unit provided in the housing and connected to the inverter circuit to detect the pressure and temperature of the refrigerant flowing through the suction passage. Heat pump device for mobile objects.
(Appendix 9)
The heat pump device for a mobile body according to appendix 8, wherein the circulation passage side detection unit detects the temperature of the refrigerant flowing upstream of the constriction part in the circulation passage.
(Appendix 10)
An accumulator is provided between the second outlet and the intake port,
The circulation passage is provided with a fixed throttle that reduces the passage area of the circulation passage,
The heat pump device for a mobile body according to appendix 2, wherein the accumulator is disposed between the housing and the evaporator.
(Appendix 11)
An accumulator is provided between the second outlet and the intake port,
The circulation passage is provided with a fixed throttle that reduces the passage area of the circulation passage,
The heat pump device for a mobile body according to supplementary note 2, wherein the evaporator is disposed between the accumulator and the electric compressor.
(Appendix 12)
An accumulator is provided between the second outlet and the intake port,
The circulation passage is provided with a fixed throttle that reduces the passage area of the circulation passage,
The heat pump device for a mobile body according to supplementary note 2, wherein the accumulator is disposed within the housing.
(Appendix 13)
a high-pressure side detection section that is provided in the housing and connected to the inverter circuit, and that detects the pressure of refrigerant flowing upstream of the fixed throttle in the circulation passage;
Any one of Supplementary Notes 10 to 12, further comprising a low-pressure side detection section provided in the housing and connected to the inverter circuit to detect the pressure and temperature of the refrigerant flowing between the accumulator and the suction port. The heat pump device for a mobile body according to item 1.
(Appendix 14)
14. The heat pump device for a moving body according to appendix 13, wherein the high-pressure side detection unit detects the temperature of the refrigerant flowing upstream of the fixed throttle in the circulation passage.
(Appendix 15)
The evaporator includes an evaporator-side first refrigerant region located downstream of the second inlet in a refrigerant flow direction;
an evaporator-side second refrigerant region located downstream of the evaporator-side first refrigerant region in the refrigerant flow direction and connected to the evaporator-side first refrigerant region and the second outlet;
an evaporator-side gas-liquid separation section located upstream of the evaporator-side first refrigerant region in the refrigerant flow direction and connected to the second inlet and the evaporator-side first refrigerant region;
an evaporator-side throttle section located between the evaporator-side first refrigerant region and the evaporator-side second refrigerant region, which reduces the pressure of the refrigerant flowing through the evaporator-side first refrigerant region;
The heat pump device for a moving body according to appendix 1 or 2, wherein the refrigerant flowing through the evaporator-side first refrigerant region and the refrigerant flowing through the evaporator-side second refrigerant region exchange heat with the cooling liquid.
(Appendix 16)
The evaporator includes an evaporator-side first refrigerant region located downstream of the second inlet in a refrigerant flow direction;
an evaporator-side second refrigerant region located downstream of the evaporator-side first refrigerant region in the flow direction of the refrigerant and connected to the evaporator-side first refrigerant region;
an evaporator-side third refrigerant region located downstream of the evaporator-side second refrigerant region in the refrigerant flow direction and connected to the evaporator-side second refrigerant region and the second outlet;
an evaporator-side gas-liquid separation section located upstream of the evaporator-side first refrigerant region in the refrigerant flow direction and connected to the second inlet and the evaporator-side first refrigerant region;
an evaporator-side throttle section located between the evaporator-side first refrigerant region and the evaporator-side second refrigerant region, which reduces the pressure of the refrigerant flowing through the evaporator-side first refrigerant region;
The refrigerant flowing through the first refrigerant region on the evaporator side exchanges heat with the refrigerant flowing through the third refrigerant region on the evaporator side,
The heat pump device for a moving body according to appendix 1 or 2, wherein the refrigerant flowing through the second refrigerant region on the evaporator side exchanges heat with the cooling liquid.
(Appendix 17)
The housing includes a heating liquid inlet that allows the heating liquid to flow into the condenser, a heating liquid outlet that allows the heating liquid to flow out of the condenser, and a heating liquid outlet that allows the cooling liquid to flow into the evaporator. 17. The heat pump device for a mobile body according to any one of appendices 1 to 16, wherein a cooling liquid inlet and a cooling liquid outlet for causing the cooling liquid to flow out of the evaporator are formed.
(Appendix 18)
At least one of the evaporator and the condenser includes a plurality of heat exchange plates and a spacer disposed between each of the heat exchange plates,
Each of the heat exchange plates, the spacer, and the housing are integrally fastened by a fastening member,
18. The heat pump device for a moving body according to any one of Supplementary Notes 1 to 17, wherein the space between each of the heat exchange plates and the spacer is sealed by the fastening force of the fastening member.
(Appendix 19)
19. The heat pump device for a mobile body according to any one of appendices 1 to 18, wherein the electric motor is disposed between the compression mechanism and the inverter circuit.
(Additional note 20)
The discharge port and the first inlet are connected by a discharge passage,
The suction port and the second outlet are connected by a suction passage,
20. The heat pump device for a moving body according to any one of appendices 1 to 19, wherein the discharge passage and the suction passage are at least partially formed in the housing.

INDUSTRIAL APPLICATION This invention can be utilized for moving objects, such as an electric vehicle.

1...Electric compressor 5...Receiver (gas-liquid separator)
6a...First pressure sensor (high pressure side detection part)
6b...First temperature sensor (high pressure side detection section)
6c...Second pressure sensor (low pressure side detection part)
6d...Second temperature sensor (low pressure side detection part)
7...Expansion valve (throttling part)
8a...Third pressure sensor (circulation passage side detection part)
8b...Third temperature sensor (circulation passage side detection section)
8c...Fourth pressure sensor (suction passage side detection part)
8d...Fourth temperature sensor (suction passage side detection part)
9, 90... Condenser 9a, 90a... First inlet 9b, 90b... First outlet 10... Housing 11, 115, 116... Evaporator 11a, 115a, 116a... Second inlet 11b, 115b, 116b... First 2 Outlet 16...Compression mechanism 16a...Suction port 16b...Discharge port 17...Electric motor 18...Inverter circuit 31...Heating liquid inlet 32...Heating liquid outlet 34...Cooling liquid inlet 35...Cooling liquid outlet 42...Accumulator 43~45...1st~3rd orifice (fixed aperture)
90e...Condenser side first refrigerant area 90f...Condenser side second refrigerant area 90h...Receiver (condenser side gas-liquid separation section)
91...First heat exchange plate (heat exchange plate)
92...First spacer (spacer)
100...Electric vehicle (mobile object)
111...Second heat exchange plate (heat exchange plate)
112...Second spacer (spacer)
115e, 116e...Evaporator side first refrigerant area 115f, 116f...Evaporator side second refrigerant area 115h, 116i...Receiver (evaporator side gas-liquid separation section)
115i, 116j...Expansion valve (evaporator side throttle part)
116g...Evaporator side third refrigerant area 201...First fastening bolt (fastening member)
203...Second fastening bolt (fastening member)
211, 212...Discharge passage 221-225...Circulation passage 231-235...Suction passage

Claims (20)

a housing; a suction port provided in the housing for sucking refrigerant; a discharge port provided in the housing for discharging refrigerant; and a discharge port provided in the housing for sucking refrigerant from the suction port. an electric compressor having a compression mechanism for discharging, and an electric motor provided in the housing for operating the compression mechanism;
a condenser that exchanges heat between the refrigerant and the heating liquid;
Equipped with an evaporator that exchanges heat between the refrigerant and the cooling liquid,
The condenser has a first inlet that allows the refrigerant discharged from the outlet to flow in, and a first outlet that allows the refrigerant to flow out toward the evaporator.
The evaporator is a heat pump device for a mobile body, which has a second inlet into which the refrigerant flowing out from the first outflow port flows, and a second outflow port into which the refrigerant flows out toward the suction port. hand,
The electric compressor is disposed between the condenser and the evaporator, and the condenser, the electric compressor, and the evaporator are integrated,
The electric compressor further includes an inverter circuit provided in the housing and controlling the electric motor,
the inverter circuit is arranged between the compression mechanism and the evaporator,
The discharge port is located closer to the condenser than the suction port,
A heat pump device for a mobile object, wherein the suction port is located closer to the evaporator than the discharge port. The first outflow port and the second inflow port are connected by a circulation passage,
The heat pump device for a moving body according to claim 1, wherein at least a portion of the circulation passage is formed in the housing. The circulation passage is provided with a gas-liquid separator and a constriction part located downstream of the gas-liquid separator in the refrigerant circulation direction to reduce the pressure of the refrigerant flowing through the circulation passage,
The heat pump device for a mobile body according to claim 2, wherein the gas-liquid separator is arranged between the housing and the condenser. The circulation passage is provided with a gas-liquid separator and a constriction part located downstream of the gas-liquid separator in the refrigerant circulation direction to reduce the pressure of the refrigerant flowing through the circulation passage,
The heat pump device for a mobile body according to claim 2, wherein the condenser is disposed between the gas-liquid separator and the electric compressor. The circulation passage is provided with a gas-liquid separator and a constriction part located downstream of the gas-liquid separator in the refrigerant circulation direction to reduce the pressure of the refrigerant flowing through the circulation passage,
The heat pump device for a mobile body according to claim 2, wherein the gas-liquid separator is arranged between the housing and the evaporator. The circulation passage is provided with a gas-liquid separator and a constriction part located downstream of the gas-liquid separator in the refrigerant circulation direction to reduce the pressure of the refrigerant flowing through the circulation passage,
The heat pump device for a mobile body according to claim 2, wherein the gas-liquid separator is disposed within the housing. The condenser includes a first refrigerant region on the condenser side connected to the first inlet;
a condenser-side second refrigerant region located downstream of the condenser-side first refrigerant region in the flow direction of the refrigerant and connected to the first outlet;
a condenser-side air outlet located between the condenser-side first refrigerant region and the condenser-side second refrigerant region and connected to the condenser-side first refrigerant region and the condenser-side second refrigerant region; It has a liquid separation part,
The refrigerant flowing through the first refrigerant region on the condenser side and the refrigerant flowing through the second refrigerant region on the condenser side exchange heat with the heating liquid,
3. The heat pump device for a moving body according to claim 2, wherein the circulation passage is provided with a constriction part that reduces the pressure of the refrigerant flowing through the circulation passage. The suction port and the second outlet are connected by a suction passage,
The circulation passage is provided with a constriction part that reduces the pressure of the refrigerant flowing through the circulation passage,
a circulation passage side detection unit that is provided in the housing and connected to the inverter circuit, and detects the pressure of refrigerant flowing upstream of the constriction part in the circulation passage;
8. The refrigerant according to any one of claims 2 to 7, further comprising: a suction passage side detection section provided in the housing and connected to the inverter circuit to detect the pressure and temperature of the refrigerant flowing through the suction passage. A heat pump device for mobile objects. 9. The heat pump device for a moving body according to claim 8, wherein the circulation passage side detection unit detects the temperature of the refrigerant flowing upstream of the constriction part in the circulation passage. An accumulator is provided between the second outlet and the intake port,
The circulation passage is provided with a fixed throttle that reduces the passage area of the circulation passage,
The heat pump device for a mobile body according to claim 2, wherein the accumulator is disposed between the housing and the evaporator. An accumulator is provided between the second outlet and the intake port,
The circulation passage is provided with a fixed throttle that reduces the passage area of the circulation passage,
The heat pump device for a mobile body according to claim 2, wherein the evaporator is arranged between the accumulator and the electric compressor. An accumulator is provided between the second outlet and the intake port,
The circulation passage is provided with a fixed throttle that reduces the passage area of the circulation passage,
The heat pump device for a moving object according to claim 2, wherein the accumulator is arranged within the housing. a high-pressure side detection section that is provided in the housing and connected to the inverter circuit, and that detects the pressure of refrigerant flowing upstream of the fixed throttle in the circulation passage;
13. The refrigerant according to claim 10, further comprising a low-pressure side detection section provided in the housing and connected to the inverter circuit to detect the pressure and temperature of the refrigerant flowing between the accumulator and the suction port. The heat pump device for a mobile body according to any one of the items. 14. The heat pump device for a mobile body according to claim 13, wherein the high-pressure side detection section detects the temperature of the refrigerant flowing upstream of the fixed throttle in the circulation passage. The evaporator includes an evaporator-side first refrigerant region located downstream of the second inlet in a refrigerant flow direction;
an evaporator-side second refrigerant region located downstream of the evaporator-side first refrigerant region in the refrigerant flow direction and connected to the evaporator-side first refrigerant region and the second outlet;
an evaporator-side gas-liquid separation section located upstream of the evaporator-side first refrigerant region in the refrigerant flow direction and connected to the second inlet and the evaporator-side first refrigerant region;
an evaporator-side throttle section located between the evaporator-side first refrigerant region and the evaporator-side second refrigerant region, which reduces the pressure of the refrigerant flowing through the evaporator-side first refrigerant region;
The heat pump device for a moving body according to claim 1 or 2, wherein the refrigerant flowing through the evaporator-side first refrigerant region and the refrigerant flowing through the evaporator-side second refrigerant region exchange heat with the cooling liquid. The evaporator includes an evaporator-side first refrigerant region located downstream of the second inlet in a refrigerant flow direction;
an evaporator-side second refrigerant region located downstream of the evaporator-side first refrigerant region in the flow direction of the refrigerant and connected to the evaporator-side first refrigerant region;
an evaporator-side third refrigerant region located downstream of the evaporator-side second refrigerant region in the refrigerant flow direction and connected to the evaporator-side second refrigerant region and the second outlet;
an evaporator-side gas-liquid separation section located upstream of the evaporator-side first refrigerant region in the refrigerant flow direction and connected to the second inlet and the evaporator-side first refrigerant region;
an evaporator-side throttle section located between the evaporator-side first refrigerant region and the evaporator-side second refrigerant region, which reduces the pressure of the refrigerant flowing through the evaporator-side first refrigerant region;
The refrigerant flowing through the first refrigerant region on the evaporator side exchanges heat with the refrigerant flowing through the third refrigerant region on the evaporator side,
The heat pump device for a moving body according to claim 1 or 2, wherein the refrigerant flowing through the second refrigerant region on the evaporator side exchanges heat with the cooling liquid. The housing includes a heating liquid inlet that allows the heating liquid to flow into the condenser, a heating liquid outlet that allows the heating liquid to flow out of the condenser, and a heating liquid outlet that allows the cooling liquid to flow into the evaporator. 3. The heat pump device for a mobile body according to claim 1, further comprising a cooling liquid inlet and a cooling liquid outlet for causing the cooling liquid to flow out of the evaporator. At least one of the evaporator and the condenser includes a plurality of heat exchange plates and a spacer disposed between each of the heat exchange plates,
Each of the heat exchange plates, the spacer, and the housing are integrally fastened by a fastening member,
The heat pump device for a mobile body according to claim 1 or 2, wherein a space between each of the heat exchange plates and the spacer is sealed by the fastening force of the fastening member. The heat pump device for a mobile body according to claim 1 or 2, wherein the electric motor is arranged between the compression mechanism and the inverter circuit. The discharge port and the first inlet are connected by a discharge passage,
The suction port and the second outlet are connected by a suction passage,
The heat pump device for a moving object according to claim 1 or 2, wherein at least a portion of the discharge passage and the suction passage are formed in the housing.

Images