Vehicle refrigeration cycle unit and vehicle air conditioning system

Abstract

Provided is a refrigeration cycle unit for vehicle which is interposed between a vehicle exterior heat exchanger and a vehicle interior heat exchanger and carries out heat exchange between secondary refrigerants flowing through the vehicle interior heat exchanger and the vehicle exterior heat exchanger, respectively, the refrigeration cycle unit for vehicle being provided with a refrigeration cycle including a compressor, a condenser, an expansion valve, and an evaporator through which a primary refrigerant sequentially flows, and the distance between the compressor and the evaporator is longer than the distance between the compressor and the condenser.

Description

Technical Field

[0001] The present disclosure relates to a refrigeration cycle unit for a vehicle and an air conditioning apparatus for a vehicle.

Background Art

[0002] Patent Document 1 discloses a refrigeration cycle that includes a compressor housed in a heat-insulating case, a heat medium cooler (evaporator )、 and a heat medium heater (condenser), and that constitutes a vehicle heat management system.

Prior Art Documents

Patent Documents

[0003]

Patent Document 1

Summary of the Invention

Problems to be Solved by the Invention

[0004] By the way, the compressor described in Patent Document 1 compresses the refrigerant flowing through the vehicle heat management system, and thus has a higher temperature than other devices. Since the compressor is disposed so as to be adjacent to the evaporator with a part of the case therebetween, heat is more easily transferred to the evaporator than to the condenser. For this reason, there is a problem in that the temperature rise of the evaporator due to the compressor becomes higher than the temperature rise of the condenser due to the compressor. When the temperature of the evaporator rises, the heat exchange performance of the evaporator deteriorates.

[0005] The present disclosure has been made to solve the above problems, and an object thereof is to provide a refrigeration cycle unit for a vehicle and an air conditioning apparatus for a vehicle that can suppress a decrease in the heat exchange efficiency of an evaporator.

Means for Solving the Problems

[0006] To solve the above problems, the vehicle refrigeration cycle unit according to the present disclosure is interposed between an outdoor heat exchanger and an indoor heat exchanger to exchange heat between the secondary refrigerants flowing through the outdoor heat exchanger and the indoor heat exchanger, respectively, and comprises a refrigeration cycle having a compressor, condenser, expansion valve, and evaporator through which a primary refrigerant flows sequentially, wherein the distance between the compressor and the evaporator is longer than the distance between the compressor and the condenser.

[0007] Furthermore, the vehicle refrigeration cycle unit according to this disclosure is interposed between an outdoor heat exchanger and an indoor heat exchanger to exchange heat between secondary refrigerants flowing through the outdoor heat exchanger and the indoor heat exchanger, respectively, and comprises a refrigeration cycle having a compressor, condenser, expansion valve, and evaporator through which a primary refrigerant flows sequentially, wherein the distance between the discharge port of the primary refrigerant in the compressor and the evaporator is longer than the distance between the discharge port and the condenser.

[0008] Furthermore, the vehicle refrigeration cycle unit according to this disclosure is interposed between an outdoor heat exchanger and an indoor heat exchanger to exchange heat between the secondary refrigerants flowing through the outdoor heat exchanger and the indoor heat exchanger, respectively, and comprises a refrigeration cycle having a compressor, condenser, expansion valve, and evaporator through which a primary refrigerant flows sequentially, wherein the length of the piping connecting the compressor and the evaporator is longer than the length of the piping connecting the compressor and the condenser.

[0009] Furthermore, the vehicle air conditioning system according to this disclosure comprises the above-mentioned vehicle refrigeration cycle unit, the above-mentioned exterior heat exchanger, and the above-mentioned interior heat exchanger. [Effects of the Invention]

[0010] According to this disclosure, it is possible to provide a vehicle refrigeration cycle unit and a vehicle air conditioning system that can suppress a decrease in the heat exchange efficiency of the evaporator. [Brief explanation of the drawing]

[0011] [Figure 1]This is a system diagram showing the configuration of a vehicle air conditioning system (during heating operation) according to the embodiment. [Figure 2] This is a plan view of a vehicle refrigeration cycle unit according to the first embodiment. [Figure 3] This is a plan view of a vehicle refrigeration cycle unit according to the second embodiment. [Figure 4] This is a plan view of a vehicle refrigeration cycle unit according to the third embodiment. [Figure 5] This is a plan view of a vehicle refrigeration cycle unit according to the fourth embodiment. [Figure 6] This is a plan view of a vehicle refrigeration cycle unit according to the fifth embodiment. [Figure 7] This is a system diagram showing the configuration of a vehicle air conditioning system (during cooling operation) according to the embodiment. [Figure 8] This is a plan view of a vehicle refrigeration cycle unit according to another embodiment. [Modes for carrying out the invention]

[0012] Hereinafter, a vehicle air conditioning system according to an embodiment of this disclosure will be described with reference to the drawings.

[0013] [First Embodiment] (Vehicle air conditioning system) Vehicle air conditioning systems are devices installed in electric vehicles and the like, and they harmonize the air inside the vehicle. These vehicle air conditioning systems adjust the temperature difference between the inside and outside of the vehicle. In this embodiment, the configuration of the vehicle air conditioning system in heating operation will be described as an example.

[0014] As shown in Figure 1, the vehicle air conditioning system 1 comprises a vehicle refrigeration cycle unit 100, an in-vehicle heat transfer medium circuit 20, and an out-vehicle heat transfer medium circuit 30. In the drawings, among the various lines (pipes) of the vehicle refrigeration cycle unit 100, the in-vehicle heat medium circuit 20, and the out-vehicle heat medium circuit 30, the lines in an open state through which the refrigerant can flow are shown by solid lines, and the lines in a closed state through which the refrigerant cannot flow are shown by broken lines. Further, various valves indicate a closed state when painted black and an open state when painted white.

[0015] (Vehicle refrigeration cycle unit) The vehicle refrigeration cycle unit 100 is a device that circulates a primary refrigerant for heat exchange with a secondary refrigerant used for in-vehicle air conditioning. In this embodiment, for example, the R290 refrigerant (propane), which is a highly flammable hydrocarbon, is adopted as the primary refrigerant.

[0016] As shown in FIG. 2, the vehicle refrigeration cycle unit 100 includes a casing 11, a refrigeration cycle 10, various lines (suction line 124, discharge line 143, pre-expansion line 136, and post-expansion line 162), and a partition portion 17.

[0017] (Casing) The casing 11 has a box shape and houses the refrigeration cycle 10, the partition portion 17, the suction line 124, the discharge line 143, the pre-expansion line 136, and the post-expansion line 162 inside.

[0018] (Refrigeration cycle) The refrigeration cycle 10 is composed of a plurality of devices that realize a thermodynamic cycle. The refrigeration cycle 10 is a refrigerant circuit that sequentially circulates and circulates the primary refrigerant through a plurality of devices while repeatedly compressing and expanding, as well as evaporating and condensing the primary refrigerant as a heat medium in order to exchange heat with the secondary refrigerant. The refrigeration cycle 10 has an evaporator 12, a compressor 14, a condenser 13, a receiver 15, and an expansion valve 16.

[0019] (Evaporator) The evaporator 12 is a plate heat exchanger that evaporates (vaporizes) the primary refrigerant by exchanging heat between the primary refrigerant flowing sequentially through the refrigeration cycle 10 and the secondary refrigerant introduced from outside the vehicle refrigeration cycle unit 100. Inside the evaporator 12, the primary refrigerant absorbs heat from the secondary refrigerant while simultaneously cooling it. The evaporator 12 is located inside the casing 11, on the bottom surface 11a of the casing 11.

[0020] (Compressor) The compressor 14 is a device that absorbs heat and compresses the vaporized primary refrigerant as it passes through the evaporator 12. The compressor 14 and the evaporator 12 are connected by an intake line 124. Specifically, one end of the intake line 124 is connected to the primary refrigerant outlet 12b of the evaporator 12, and the other end of the intake line 124 is connected to the intake port 14b of the compressor 14.

[0021] The pressure of the primary refrigerant introduced into the compressor 14 is increased by the compression of the compressor 14 to a predetermined pressure higher than the pressure before compression. As a result, the temperature of the primary refrigerant rises above the temperature before compression.

[0022] The compressor 14 has a compressor casing 14a, an inlet 14b, and a discharge port 14c. The compressor casing 14a is cylindrical in shape and is positioned to extend from the bottom surface 11a of the casing 11 in the direction of gravity G. The compressor 14 in this embodiment is a so-called vertically mounted compressor. A refrigerant compression mechanism is formed inside the compressor casing 14a.

[0023] The suction port 14b is a refrigerant inlet for introducing refrigerant into the compressor casing 14a. The suction port 14b is located at the lower end of the compressor casing 14a in the direction of gravity G. The primary refrigerant is introduced into the compressor casing 14a through this suction port 14b.

[0024] The discharge port 14c is a refrigerant outlet for discharging refrigerant from the compressor casing 14a. The discharge port 14c is located at the end of the compressor casing 14a that is upward in the direction of gravity G. The primary refrigerant is discharged to the outside of the compressor casing 14a through this discharge port 14c. The discharge port 14c is the part of the compressor 14 that reaches the highest temperature.

[0025] (Condenser) The condenser 13 is a plate heat exchanger that condenses (liquefies) the primary refrigerant by exchanging heat between the primary refrigerant, which has become hotter and higher in pressure than before it was compressed by passing through the compressor 14, and the secondary refrigerant introduced from outside the vehicle refrigeration cycle unit 100. The condenser 13 is located inside the casing 11 and is installed on the bottom surface 11a of the casing 11.

[0026] The condenser 13 and the compressor 14 are connected by a discharge line 143. Specifically, one end of the discharge line 143 is connected to the discharge port 14c of the compressor 14, and the other end of the discharge line 143 is connected to the primary refrigerant inlet 13a of the condenser 13. Inside the condenser 13, the primary refrigerant is cooled by the secondary refrigerant, and at the same time, the temperature of the secondary refrigerant is increased.

[0027] The primary refrigerant, in a gaseous state, introduced into the condenser 13 is cooled by the secondary refrigerant, and after passing through a two-phase state of gas-liquid mixture, it transitions to a liquid state. Therefore, the primary refrigerant that has passed through the condenser 13 becomes a fluid in a liquid-liquid mixture state.

[0028] The condenser 13 is positioned inside the casing 11 adjacent to the compressor 14. In this embodiment, the direction in which the condenser 13 is adjacent to the compressor 14 (left-right direction in Figure 2) is referred to as the first adjacent direction H1, and the direction perpendicular to the first adjacent direction H1 (up-down direction in Figure 2) is referred to as the second adjacent direction H2. These first adjacent direction H1 and second adjacent direction H2 are perpendicular to the direction of gravity G. Therefore, the horizontal direction is defined by the first adjacent direction H1 and the second adjacent direction H2.

[0029] Here, the evaporator 12 is adjacent to the condenser 13 from one side in the second adjacent direction H2. While the condenser 13 is adjacent to the compressor 14 in the first adjacent direction H1, the evaporator 12 is only horizontally separated from the compressor 14 and is not adjacent to the compressor 14 in either the first adjacent direction H1 or the second adjacent direction H2. Therefore, the distance between the compressor 14 and the evaporator 12 is longer than the distance between the compressor 14 and the condenser 13.

[0030] Furthermore, in this embodiment, the discharge port 14c of the compressor 14 faces the condenser 13 in the first adjacent direction H1. Therefore, the distance between the primary refrigerant discharge port 14c of the compressor 14 and the evaporator 12 is longer than the distance between the discharge port 14c and the condenser 13. More specifically, the length of the piping connecting the compressor 14 and the evaporator 12, i.e., the suction line 124, is longer than the length of the piping connecting the compressor 14 and the condenser 13, i.e., the discharge line 143.

[0031] Furthermore, "adjacent in the first adjacent direction H1" means that of two objects placed side by side inside the casing 11, more than half of the dimension of one object in the second adjacent direction H2 overlaps with the dimension of the other object in the second adjacent direction H2 when viewed from the first adjacent direction H1. Also, "adjacent in the second adjacent direction H2" means that of two objects placed side by side inside the casing 11, more than half of the dimension of one object in the first adjacent direction H1 overlaps with the dimension of the other object in the first adjacent direction H1 when viewed from the second adjacent direction H2.

[0032] (receiver) The receiver 15 is a gas-liquid separator that receives the primary refrigerant, which has become a gas-liquid mixed fluid after passing through the condenser 13, separates this primary refrigerant into a gas phase and a liquid phase, and temporarily holds them inside. The receiver 15 is located inside the casing 11 and is installed on the bottom surface 11a of the casing 11.

[0033] The receiver 15 and the condenser 13 are connected by the first line 135 of the pre-expansion line 136. Specifically, one end of the first line 135 is connected to the primary refrigerant outlet 13b of the condenser 13, and the other end of the first line 135 is connected to the refrigerant inlet of the receiver 15.

[0034] The primary refrigerant, in a gas-liquid mixture state, introduced into the receiver 15 flows into the liquid phase portion stored inside the receiver 15. The liquid portion of the incoming primary refrigerant is added to the liquid phase, while the remaining gaseous portion moves upward as bubbles inside the receiver 15 and is added to the gas phase. The primary refrigerant stored as a liquid phase inside the receiver 15 is discharged to the outside of the receiver 15. In this way, liquid primary refrigerant is always supplied from the receiver 15.

[0035] (Expansion valve) The expansion valve 16 is a device that receives the primary refrigerant, which has become liquid after passing through the receiver 15, and adiabatically expands this primary refrigerant. The expansion valve 16 is located inside the casing 11 and is installed on the bottom surface 11a of the casing 11. The expansion valve 16 and the receiver 15 are connected by a second line 156 of the pre-expansion line 136. That is, one end of the second line 156 is connected to the refrigerant outlet of the receiver 15, and the other end of the second line 156 is connected to the expansion valve 16.

[0036] The pressure of the primary refrigerant introduced into the expansion valve 16 is reduced to a predetermined pressure lower than before expansion by the expansion action of the expansion valve 16. As a result, the temperature of the primary refrigerant decreases compared to before expansion. Specifically, the primary refrigerant that has passed through the expansion valve 16 becomes a liquid fluid and its temperature drops to a level lower than that of the secondary refrigerant, which is the recipient of the heat exchange.

[0037] The expansion valve 16 and the evaporator 12 are connected by an expansion line 162, and the primary refrigerant that has passed through the expansion valve 16 is introduced into the evaporator 12 through this expansion line 162. That is, one end of the expansion line 162 is connected to the expansion valve 16, and the other end of the expansion line 162 is connected to the primary refrigerant inlet 12a of the evaporator 12.

[0038] (Partition wall) The partition wall 17 is an insulating material provided inside the casing 11 between the evaporator 12 and the condenser 13. The thermal conductivity of the partition wall 17 is lower than that of the casing 11. In this embodiment, the partition wall 17 has a partition plate 17a which is a plate member that stands upright from the bottom surface 11a of the casing 11 toward the upward direction of gravity G, and separates the evaporator 12 and the condenser 13. That is, the longitudinal direction of the partition plate 17a coincides with the first adjacent direction H1. This suppresses heat transfer through air between the evaporator 12 and the condenser 13. Specifically, the partition plate 17a provided on the bottom surface 11a between the evaporator 12 and the condenser 13 suppresses heat conduction through the bottom of the casing 11 that constitutes the bottom surface 11a, convection of air inside the casing 11, and heat radiation from the condenser 13 toward the evaporator 12. In this embodiment, heat conduction, convection, and thermal radiation are collectively referred to as "heat transfer." The material used to constitute the partition plate 17a is, for example, rubber or resin. a This may be formed from the same material as the casing 11.

[0039] (In-vehicle heat transfer fluid circuit) The in-vehicle heat transfer fluid circuit 20 is a refrigerant circuit that circulates the secondary refrigerant, which has exchanged heat with the primary refrigerant in the refrigeration cycle 10, and also harmonizes the air inside the vehicle. In this embodiment, an antifreeze such as ethylene glycol is used as the secondary refrigerant (coolant).

[0040] As shown in Figure 1, the in-vehicle heat transfer medium circuit 20 includes a heater core 21a (in-vehicle heat exchanger 21), a cooler core 21b (in-vehicle heat exchanger 21), a first pump 22, a first valve 23, a second valve 24, and various lines (first heat transfer medium line 20a to seventh heat transfer medium line 20g).

[0041] The heater core 21a and the cooler core 21b are heat exchangers for exchanging heat between the indoor air inside the vehicle body C and the outdoor air outside the vehicle body C, and the secondary refrigerant. The secondary refrigerant, which has passed through the condenser 13 of the vehicle refrigeration cycle unit 100, is introduced into the heater core 21a. In the process of introducing the secondary refrigerant from the condenser 13 to the heater core 21a, the secondary refrigerant passes through the first pump 22 and the first valve 23.

[0042] The first pump 22 is a pump that pumps the secondary refrigerant, which has passed through the condenser 13, to the heater core 21a. The first heat transfer medium line 20a, which serves as a flow path for drawing the secondary refrigerant into the first pump 22, connects the condenser 13 and the first pump 22. Specifically, one end of the first heat transfer medium line 20a is connected to the secondary refrigerant outlet 13d of the condenser 13, and the other end of the first heat transfer medium line 20a is connected to the refrigerant inlet of the first pump 22.

[0043] The second heat transfer fluid line 20b, which serves as a flow path for discharging the secondary refrigerant from the first pump 22 toward the heater core 21a, connects the first pump 22 and the first valve 23. That is, one end of the second heat transfer fluid line 20b is connected to the refrigerant discharge port of the first pump 22, and the other end of the second heat transfer fluid line 20b is connected to the first valve 23. The first valve 23 is a three-way valve that can change the flow path (destination) of the secondary refrigerant.

[0044] The first valve 23 and the heater core 21a are connected by a third heat transfer fluid line 20c. Specifically, one end of the third heat transfer fluid line 20c is connected to the first valve 23, and the other end of the third heat transfer fluid line 20c is connected to the heater core 21a.

[0045] The secondary refrigerant introduced into the heater core 21a is cooled by heat exchange with the indoor air and the outdoor air introduced into the vehicle body C, and at the same time raises the temperature of this indoor and outdoor air. This warms the air inside the vehicle body C. The outdoor air used is, for example, outside air from outside the vehicle body C introduced by a blower (not shown) positioned in front of the heater core 21a and cooler core 21b.

[0046] The secondary refrigerant cooled in the heater core 21a is returned to the condenser 13 via the second valve 24. The second valve 24 is a three-way valve that can change the flow path (destination) of the secondary refrigerant. Second valve 24 The heater core 21a is connected to the heater core 21a by a fourth heat transfer fluid line 20d. Specifically, one end of the fourth heat transfer fluid line 20d is connected to the refrigerant outlet of the heater core 21a, and the other end of the fourth heat transfer fluid line 20d is connected to the second valve 24.

[0047] The second valve 24 and the condenser 13 are connected by a fifth heat transfer medium line 20e. Specifically, one end of the fifth heat transfer medium line 20e is connected to the second valve 24, and the other end of the fifth heat transfer medium line 20e is connected to the secondary refrigerant inlet 13c of the condenser 13.

[0048] With the configuration described above, the secondary refrigerant flows sequentially through the condenser 13, the first pump 22, and the heater core 21a, and then returns to the condenser 13. This circulation is repeated, enabling heating operation and maintaining the temperature rise inside the vehicle.

[0049] Here, the cooler core 21b is installed inside the vehicle body C, independently of the heater core 21a. During cooling operation, secondary refrigerant that has passed through the evaporator 12 is introduced into the cooler core 21b, and heat exchange occurs between this secondary refrigerant and the outside air. The flow of the secondary refrigerant during cooling operation will be described later.

[0050] (Vehicle outside heat medium circuit) The external heat transfer fluid circuit 30 is a refrigerant circuit that circulates the secondary refrigerant that has exchanged heat with the primary refrigerant in the refrigeration cycle 10, and also cools the battery for driving the vehicle body. The external heat transfer fluid circuit 30 includes an external heat exchanger 31, a second pump 32, various valves (third valve 33 and fifth valve 35), a battery cooler 36, and various lines (eighth heat transfer fluid line 30a to twelfth heat transfer fluid line 30e, and first connection line 30f to fourth connection line 30i).

[0051] The vehicle's outdoor heat exchanger 31 is a heat exchanger for exchanging heat between the outdoor air and the secondary refrigerant. A portion of the secondary refrigerant that has passed through the evaporator 12 of the vehicle's refrigeration cycle unit 100 is introduced into the vehicle's outdoor heat exchanger 31 via the third valve 33. The remaining portion of the secondary refrigerant that has passed through the evaporator 12 is introduced into the battery cooler 36 via the fourth valve 34.

[0052] The evaporator 12, the third valve 33, and the fourth valve 34 are connected by an eighth heat transfer fluid line 30a. Specifically, one end of the eighth heat transfer fluid line 30a is connected to the secondary refrigerant outlet 12d of the evaporator 12, and the other end of the eighth heat transfer fluid line 30a branches into two directions midway through the line and is connected to the third valve 33 and the fourth valve 34, respectively. These third valve 33 and fourth valve 34 are three-way valves that can change the flow path (destination) of the secondary refrigerant.

[0053] The third valve 33 and the outdoor heat exchanger 31 are connected by the ninth heat medium line 30b. Specifically, one end of the ninth heat medium line 30b is connected to the third valve 33, and the other end of the ninth heat medium line 30b is connected to the refrigerant inlet of the outdoor heat exchanger 31.

[0054] The secondary refrigerant introduced into the vehicle's outdoor heat exchanger 31 through the eighth heat transfer medium line 30a, the third valve 33, and the ninth heat transfer medium line 30b absorbs heat by exchanging heat with the outside air. As a result, the temperature of the secondary refrigerant becomes higher than that of the primary refrigerant introduced into the evaporator 12, thereby raising the temperature of the primary refrigerant circulating in the refrigeration cycle 10 within the evaporator 12. The outside air, which is the destination of the heat exchange in the vehicle's outdoor heat exchanger 31, is drawn in from outside the vehicle body C through the front grille F by a blower B located on the front side inside the vehicle body C.

[0055] The second pump 32 is a pump that pressurizes the secondary refrigerant, whose temperature has risen by the outdoor heat exchanger 31, and sends it to the evaporator 12. The secondary refrigerant, after passing through the outdoor heat exchanger 31, passes through the fifth valve 35 in the process of being drawn into the second pump 32. The fifth valve 35 is a three-way valve that can change the flow path (destination) of the secondary refrigerant.

[0056] The fifth valve 35 and the outdoor heat exchanger 31 are connected by the tenth heat medium line 30c. That is, one end of the tenth heat medium line 30c is connected to the outdoor heat exchanger 31, and the other end of the tenth heat medium line 30c is connected to the fifth valve 35.

[0057] The eleventh heat transfer fluid line 30d, which serves as a passage for drawing secondary refrigerant into the second pump 32, connects the fifth valve 35 and the second pump 32. That is, one end of the eleventh heat transfer fluid line 30d is connected to the fifth valve 35, and the other end of the eleventh heat transfer fluid line 30d is connected to the second pump 32.

[0058] The second pump 32 and the evaporator 12 are connected by a twelfth heat transfer fluid line 30e. That is, one end of the twelfth heat transfer fluid line 30e is connected to the second pump 32, and the other end of the twelfth heat transfer fluid line 30e is connected to the secondary refrigerant inlet 12c of the evaporator 12. 32 The secondary refrigerant, which has been pressurized, is introduced into the evaporator 12.

[0059] With the configuration described above, the secondary refrigerant flows sequentially through the evaporator 12, the outdoor heat exchanger 31, and the second pump 32, and then returns to the evaporator 12. This circulation is repeated, which helps maintain the temperature rise of the primary refrigerant circulating in the refrigeration cycle 10 through heat exchange in the evaporator 12.

[0060] Therefore, the vehicle refrigeration cycle unit 100 is interposed between the outdoor heat exchanger 31 and the heater core 21a (indoor heat exchanger 21), and performs heat exchange between the secondary refrigerants flowing through the outdoor heat exchanger 31 and the indoor heat exchanger 21, respectively.

[0061] The battery cooler 36 is a heat exchanger for cooling the battery. The battery cooler 36 is installed inside the vehicle body C. The remaining portion of the secondary refrigerant, which is cooled by the evaporator 12 and flows through the eighth heat transfer medium line 30a, is introduced into the battery cooler 36 via the fourth valve 34. The fourth valve 34 and the battery cooler 36 are connected by a first connection line 30f. That is, one end of the first connection line 30f is connected to the fourth valve 34, and the other end of the first connection line 30f is connected to the refrigerant inlet of the battery cooler 36.

[0062] The secondary refrigerant, warmed by heat exchange with the battery (not shown) in the battery cooler 36, is returned to the evaporator 12. The battery cooler 36 and the eleventh heat transfer medium line 30d are connected by a second connection line 30g. Specifically, one end of the second connection line 30g is connected to the refrigerant outlet of the battery cooler 36, and the other end of the second connection line 30g is connected to the portion of the eleventh heat transfer medium line 30d closer to the fifth valve 35 than the second pump 32. Therefore, the secondary refrigerant that has passed through the battery cooler 36 joins the eleventh heat transfer medium line 30d via the second connection line 30g and is then pumped back to the evaporator 12 by the second pump 32.

[0063] Here, the fourth valve 34 and the cooler core 21b are connected by the sixth heat transfer fluid line 20f. That is, one end of the sixth heat transfer fluid line 20f is connected to the fourth valve 34, and the other end of the sixth heat transfer fluid line 20f is Coolacore 21b It is connected to the refrigerant inlet. Furthermore, the cooler core 21b and the second connection line 30g are connected by the seventh heat transfer fluid line 20g. That is, one end of the seventh heat transfer fluid line 20g is connected to the cooler core 21b, and the other end of the seventh heat transfer fluid line 20g is connected to the second connection line 30g. ru.

[0064] During heating operation, the fourth valve 34 directs the secondary refrigerant flowing in from the eighth heat transfer medium line 30a only to the first connection line 30f, and not to the sixth heat transfer medium line 20f. In other words, the fourth valve 34 supplies the secondary refrigerant only to the battery cooler 36, and not to the cooler core 21b.

[0065] Furthermore, the first valve 23 and the fifth valve 35 are connected by a third connecting line 30h. That is, one end of the third connecting line 30h is connected to the first valve 23, and the other end of the third connecting line 30h is connected to the fifth valve 35.

[0066] During heating operation, the first valve 23 directs the secondary refrigerant flowing in from the second heat transfer medium line 20b only to the third heat transfer medium line 20c, and not to the third connection line 30h. The fifth valve 35 directs the secondary refrigerant flowing in from the tenth heat transfer medium line 30c only to the eleventh heat transfer medium line 30d, and not to the third connection line 30h.

[0067] Furthermore, the second valve 24 and the third valve 33 are connected by a fourth connecting line 30i. That is, one end of the fourth connecting line 30i is connected to the second valve 24, and the other end of the fourth connecting line 30i is connected to the third valve 33.

[0068] During heating operation, the second valve 24 directs the secondary refrigerant flowing in from the fourth heat medium line 20d only to the fifth heat medium line 20e, and not to the fourth connection line 30i. The third valve 33 directs the secondary refrigerant flowing in from the eighth heat medium line 30a only to the ninth heat medium line 30b, and not to the fourth connection line 30i.

[0069] (Effects and Benefits) In the vehicle refrigeration cycle unit 100 according to the above embodiment, the distance between the compressor 14 and the evaporator 12 constituting the refrigeration cycle 10 is longer than the distance between the compressor 14 and the condenser 13. Therefore, the amount of heat, such as radiant heat, transferred from the compressor 14 to the evaporator 12 is less than the amount of heat transferred to the condenser 13. As a result, the temperature rise of the evaporator 12 caused by the compressor 14 can be suppressed more than the temperature rise of the condenser 13 caused by the compressor 14. Consequently, a decrease in the heat exchange efficiency between the primary refrigerant and the secondary refrigerant in the evaporator 12 can be suppressed.

[0070] Furthermore, in the vehicle refrigeration cycle unit 100 according to the above embodiment, the distance between the primary refrigerant discharge port 14c of the compressor 14 and the evaporator 12 is longer than the distance between the discharge port 14c and the condenser 13. Therefore, the amount of heat, such as radiant heat, transmitted from the discharge port 14c of the compressor 14 to the evaporator 12 is less than the amount of radiant heat transmitted to the condenser 13. This allows for the same effects as described above to be achieved.

[0071] Furthermore, in the vehicle refrigeration cycle unit 100 according to the above embodiment, the length of the piping connecting the compressor 14 and the evaporator 12 is longer than the length of the piping connecting the compressor 14 and the condenser 13. Therefore, heat is less likely to be transferred from the compressor 14 to the evaporator 12 through these pipes. This allows for the same effects as described above to be achieved.

[0072] Furthermore, the vehicle refrigeration cycle unit 100 according to the above embodiment is equipped with a partition wall 17 between the condenser 13 and the evaporator 12, which separates the condenser 13 and the evaporator 12. This partition wall 17 can suppress heat transfer from the condenser 13 to the evaporator 12. As a result, the temperature rise of the evaporator caused by the condenser can be suppressed.

[0073] Furthermore, since the partition wall portion 17 of the vehicle refrigeration cycle unit 100 according to the above embodiment is a plate member, heat transfer from the condenser 13 to the evaporator 12 can be suppressed with a simple configuration of a plate member.

[0074] [Second Embodiment] The following describes a vehicle air conditioning system 1 according to the second embodiment of this disclosure. The vehicle refrigeration cycle unit 100 described in the second embodiment differs from the vehicle refrigeration cycle unit 100 of the first embodiment in the configuration of the partition wall 17. Components similar to those in the first embodiment are denoted by the same reference numerals and detailed descriptions are omitted.

[0075] (Partition wall) As shown in Figure 3, the partition wall 17 is an insulating material provided inside the casing 11 between the evaporator 12 and the condenser 13. In this embodiment, the partition wall 17 has a housing 17b that houses only the compressor 14 and the condenser 13, which are the three components of the refrigeration cycle 10. That is, the casing 11 and the housing 17b are nested inside each other. The partition wall of this housing 17b suppresses heat transfer between the evaporator 12 and the condenser 13. For example, rubber or resin can be used as the material that makes up the housing 17b.

[0076] (Effects and Benefits) In the vehicle refrigeration cycle unit 100 according to the above embodiment, heat such as radiant heat generated from the compressor 14 and condenser 13 can be retained within the housing 17b. As a result, the amount of heat transferred from the compressor 14 to the evaporator 12 is less than the amount of heat transferred to the condenser 13. Therefore, the same effects as in the first embodiment can be achieved.

[0077] [Third Embodiment] The following describes a vehicle air conditioning system 1 according to the third embodiment of this disclosure. third The vehicle refrigeration cycle unit 100 described in this embodiment differs from the vehicle refrigeration cycle unit 100 of the first embodiment in the positional relationship (arrangement) of the evaporator 12, compressor 14, and condenser 13 within the casing 11. Components similar to those in the first embodiment are denoted by the same reference numerals and detailed descriptions are omitted.

[0078] (Condenser) As shown in Figure 4, the condenser 13 is positioned inside the casing 11 adjacent to the compressor 14. Hereinafter, in this embodiment, the direction in which the condenser 13 is adjacent to the compressor 14 (vertical direction in Figure 4) will be referred to as the second adjacent direction H2, and the direction perpendicular to the second adjacent direction H2 (horizontal direction in Figure 4) will be referred to as the first adjacent direction H1. These first adjacent direction H1 and second adjacent direction H2 are gravity The directions are orthogonal. That is, the horizontal direction is defined by the first adjacent direction H1 and the second adjacent direction H2.

[0079] Here, the evaporator 12 is adjacent to the condenser 13 from one side of the second adjacent direction H2, and the compressor 14 is adjacent to the condenser 13 from the other side of the second adjacent direction H2. That is, the condenser 13 is located between the compressor 14 and the evaporator 12. Therefore, the distance between the compressor 14 and the evaporator 12 is longer than the distance between the compressor 14 and the condenser 13.

[0080] Furthermore, in this embodiment, the discharge port 14c of the compressor 14 faces one side in the first adjacent direction H1, and the distance between the discharge port 14c and the evaporator 12 is longer than the distance between the discharge port 14c and the condenser 13. More specifically, the length of the piping connecting the compressor 14 and the evaporator 12, i.e., the suction line 124, is longer than the length of the piping connecting the compressor 14 and the condenser 13, i.e., the discharge line 143.

[0081] (Effects and Benefits) In the vehicle refrigeration cycle unit 100 according to the above embodiment, a condenser 13 is positioned between the compressor 14 and the evaporator 12. Therefore, the amount of heat, such as radiant heat, transferred from the compressor 14 to the evaporator 12 is less than the amount of heat transferred to the condenser 13. Consequently, the same effects as in the first embodiment can be achieved.

[0082] [Fourth Embodiment] The following describes a vehicle air conditioning system 1 according to the fourth embodiment of this disclosure. The vehicle refrigeration cycle unit 100 described in the fourth embodiment differs from the vehicle refrigeration cycle unit 100 of the third embodiment in the configuration of the partition wall 17. Components similar to those in the third embodiment are denoted by the same reference numerals and detailed descriptions are omitted.

[0083] (Partition wall) As shown in Figure 5, the partition wall 17 is an insulating material provided inside the casing 11 between the evaporator 12 and the condenser 13. In this embodiment, the partition wall 17 has a housing 17b that houses only the compressor 14 and the condenser 13, which are the three components of the refrigeration cycle 10. That is, the casing 11 and the housing 17b are nested inside each other. The partition wall of this housing 17b suppresses direct heat transfer between the evaporator 12 and the condenser 13 via air.

[0084] (Effects and Benefits) In the vehicle refrigeration cycle unit 100 according to the above embodiment, heat such as radiant heat generated from the compressor 14 and condenser 13 can be retained within the housing 17b. As a result, the amount of heat transferred from the compressor 14 to the evaporator 12 is less than the amount of heat transferred to the condenser 13. Therefore, the same effects as in the first embodiment can be achieved.

[0085] [Fifth Embodiment] The following describes a vehicle air conditioning system 1 according to the fifth embodiment of this disclosure. The vehicle refrigeration cycle unit 100 described in the fifth embodiment differs from the vehicle refrigeration cycle unit 100 of the first embodiment in the arrangement of the compressor 14. Components similar to those in the first embodiment are denoted by the same reference numerals and detailed descriptions are omitted.

[0086] (Compressor) As shown in Figure 6, the compressor 14 has a compressor casing 14a, an inlet 14b, and a discharge port 14c. The compressor casing 14a is cylindrical in shape and is positioned to extend in the second adjacent direction H2 from the bottom surface 11a of the casing 11 inside the casing 11. The compressor 14 in this embodiment is a so-called horizontally mounted compressor. A refrigerant compression mechanism is formed inside the compressor casing 14a.

[0087] The suction port 14b is a refrigerant inlet for introducing refrigerant into the compressor casing 14a. The suction port 14b is located at one end of the compressor casing 14a in the second adjacent direction H2. That is, the suction port 14b is located between the evaporator 12 and the condenser 13. Evaporator 12 It is located on the side of the compressor casing 14a. The primary refrigerant is introduced into the compressor casing 14a through this intake port 14b. The intake port 14b is the part of the compressor 14 where the temperature is lowest.

[0088] The discharge port 14c is a refrigerant outlet for discharging refrigerant from the compressor casing 14a. The discharge port 14c is located at the other end of the compressor casing 14a in the second adjacent direction H2. That is, the discharge port 14c is located between the evaporator 12 and the condenser 13. Condenser 13 It is located in the compressor casing 14a on the side. The primary refrigerant is discharged to the outside of the compressor casing 14a through this discharge port 14c. The discharge port 14c is the part of the compressor 14 that is the hottest. Therefore, the compressor casing 14a has a temperature distribution in which the temperature gradually increases from the intake port 14b side to the discharge port 14c side.

[0089] (Effects and Benefits) In the above embodiment of the vehicle refrigeration cycle unit 100, the intake port 14b is one of the evaporator 12 and the condenser 13, Evaporator 12 It is provided on the side of the compressor casing 14a, and the discharge port 14c is Condenser 13 Since it is located in the compressor casing 14a on the side, the amount of heat, such as radiant heat, transferred from the compressor 14 to the evaporator 12 is less than the amount of heat transferred to the condenser 13. Therefore, the same effects as in the first embodiment can be achieved.

[0090] [Other embodiments] While embodiments of this disclosure have been described in detail above with reference to the drawings, the specific configurations are not limited to those of each embodiment, and additions, omissions, substitutions, and other modifications to the configurations are permitted without departing from the gist of this disclosure. Furthermore, this disclosure is not limited by the embodiments, but only by the claims.

[0091] In the above embodiment, the configuration when the vehicle air conditioning system 1 is in heating operation was described as an example, but it is not limited to heating operation, and the same configuration as in the above embodiment can be adopted for the vehicle refrigeration cycle unit 100 even when performing cooling operation. The configurations of the in-vehicle heat transfer fluid circuit 20 and the out-vehicle heat transfer fluid circuit 30 during air conditioning operation will be described below with reference to Figure 7.

[0092] The first pump 22 pumps the secondary refrigerant condensed by the condenser 13 to the outdoor heat exchanger 31. The first heat transfer fluid line 20a, which serves as a flow path for drawing the secondary refrigerant into the first pump 22, connects the condenser 13 and the first pump 22.

[0093] The second heat transfer medium line 20b, which serves as a flow path for discharging the secondary refrigerant from the first pump 22 toward the outdoor heat exchanger 31, connects the first pump 22 and the first valve 23. Here, the first valve 23 prevents the secondary refrigerant discharged from the first pump 22 from flowing into the third heat transfer medium line 20c. Third connection line 30h Dispose of it. Third connection line 30h The secondary refrigerant that flowed into it was Fifth valve 35 It flows into.

[0094] Here, Fifth valve 35 teeth, Third connection line 30h The secondary refrigerant flowing in is not directed to the eleventh heat transfer medium line 30d, but instead flows to the tenth heat transfer medium line 30c. The secondary refrigerant that flows into the tenth heat transfer medium line 30c then flows into the vehicle's outdoor heat exchanger 31.

[0095] The secondary refrigerant that has passed through the outdoor heat exchanger 31 is delivered via the ninth heat transfer medium line 30b. Third valve 33It flows into. Therefore, the vehicle air conditioning system 1 cooling During operation, the flow direction of the secondary refrigerant through the tenth heat transfer medium line 30c, the outdoor heat exchanger 31, and the ninth heat transfer medium line 30b is opposite to the flow direction of the secondary refrigerant during heating operation.

[0096] Here, Third valve 33 This means that the secondary refrigerant flowing in from the ninth heat transfer fluid line 30b is not flowed into the eighth heat transfer fluid line 30a. Fourth connection line 30i Dispose of it. Fourth connection line 30i The secondary refrigerant that flows into the valve flows into the second valve 24.

[0097] Here, the second valve 24 is Fourth connection line 30i The secondary refrigerant flowing in is not directed to the fourth heat transfer medium line 20d, but instead flows to the fifth heat transfer medium line 20e. The secondary refrigerant flowing into the fifth heat transfer medium line 20e then flows into the condenser 13.

[0098] With the configuration described above, the secondary refrigerant flows sequentially through the condenser 13, the first pump 22, and the outdoor heat exchanger 31, before returning to the condenser 13. This circulation is repeated, allowing the primary refrigerant circulating in the refrigeration cycle 10 to be continuously cooled by the heat exchange in the condenser 13.

[0099] The second pump 32 pressurizes the secondary refrigerant cooled by the evaporator 12 to the cooler core 21b. Due to the suction force of the pump, the secondary refrigerant that has passed through the evaporator 12 flows into the eighth heat transfer medium line 30a. Fourth valve 34 It flows into here. Fourth valve 34 This allows the secondary refrigerant flowing in from the eighth heat transfer fluid line 30a to flow into both the sixth heat transfer fluid line 20f and the first connection line 30f.

[0100] The secondary refrigerant that flows into the sixth heat transfer medium line 20f flows into the cooler core 21b. After heat exchange is complete in the cooler core 21b, the secondary refrigerant flows into the seventh heat transfer medium line 20g, and then into the second connection line 30g. The secondary refrigerant that flows into the second connection line 30g flows into the eleventh heat transfer medium line 30d, and returns to the evaporator 12 via the second pump 32 and the twelfth heat transfer medium line 30e.

[0101] The secondary refrigerant that flows into the first connection line 30f flows into the battery cooler 36. Therefore, the battery cooler 36 exchanges heat with the secondary refrigerant (is cooled) during both heating and cooling operation of the vehicle air conditioning system 1. The secondary refrigerant that has finished heat exchange in the battery cooler 36 flows into the second connection line 30g. The secondary refrigerant that has flowed into the second connection line 30g flows into the eleventh heat medium line 30d, and returns to the evaporator 12 via the second pump 32 and the twelfth heat medium line 30e.

[0102] With the configuration described above, the secondary refrigerant flows sequentially through the evaporator 12, the cooler core 21b, and the second pump 32, and then returns to the evaporator 12. This circulation is repeated, enabling cooling operation and keeping the interior of the vehicle cool.

[0103] Furthermore, the partition plate 17a of the partition wall 17 in the above embodiments is not limited to the configurations of the first and third embodiments. For example, as shown in Figure 8, the partition plate 17a may be arranged to separate the condenser 13 and the evaporator 12, and also to separate the expansion valve 16 and the evaporator 12 inside the casing 11. This can further suppress heat transfer to the evaporator 12.

[0104] Furthermore, while R290 refrigerant was used as an example of the primary refrigerant and ethylene glycol as an example of the secondary refrigerant in the above embodiment, other refrigerants may be used for the primary and secondary refrigerants.

[0105] Furthermore, the external heat transfer medium circuit 30 in the above embodiment may further include a drive motor cooler (not shown), which is a heat exchanger for cooling the drive motor, and an inverter cooler (not shown), which is a heat exchanger for cooling the inverter (power converter). In this case, the secondary refrigerant that has passed through the external heat exchanger 31 is introduced into the drive motor cooler and the inverter cooler, respectively, as cooling water for cooling the drive motor and the inverter, through piping (not shown) connecting the external heat exchanger 31 to the drive motor cooler and the inverter cooler. Furthermore, the secondary refrigerant that has been heated by heat exchange in the drive motor cooler and the inverter cooler may flow into the eleventh heat transfer medium line 30d through piping, similar to the secondary refrigerant that flows through the second connection line 30g from the battery cooler 36 toward the eleventh heat transfer medium line 30d.

[0106] Furthermore, the vehicle refrigeration cycle unit 100 in the above embodiment may have an upper surface facing upward in the direction of gravity G, and may further include a bracket that fixes the evaporator 12, compressor 14, and condenser 13 to this upper surface while being interposed between the refrigeration cycle 10 and the bottom surface 11a of the casing 11. In this case, the bracket fixes the refrigeration cycle 10 to the upper surface while being fixed to an inner wall surface, for example, in the front compartment outside the vehicle. Therefore, the refrigeration cycle 10 may be configured to be provided on the bottom surface 11a of the casing 11 via the bracket. In this case, the thermal conductivity of the partition wall 17 is lower than that of the bracket.

[0107] [Note] The vehicle refrigeration cycle unit and vehicle air conditioning system described in the above embodiment can be understood, for example, as follows.

[0108] (1) The vehicle refrigeration cycle unit 100 according to the first embodiment is a vehicle refrigeration cycle unit 100 interposed between an outdoor heat exchanger 31 and an indoor heat exchanger 21, which exchanges heat between the secondary refrigerants flowing through the outdoor heat exchanger 31 and the indoor heat exchanger 21, and comprises a refrigeration cycle 10 having a compressor 14, a condenser 13, an expansion valve 16, and an evaporator 12 through which a primary refrigerant flows sequentially, wherein the distance between the compressor 14 and the evaporator 12 is longer than the distance between the compressor 14 and the condenser 13.

[0109] As a result, the amount of heat, such as radiant heat, transferred from the compressor 14 to the evaporator 12 is less than the amount of heat transferred to the condenser 13.

[0110] (2) The vehicle refrigeration cycle unit 100 according to the second embodiment is a vehicle refrigeration cycle unit 100 interposed between an outdoor heat exchanger 31 and an indoor heat exchanger 21, which exchanges heat between the secondary refrigerants flowing through the outdoor heat exchanger 31 and the indoor heat exchanger 21, and comprises a refrigeration cycle 10 having a compressor 14, a condenser 13, an expansion valve 16, and an evaporator 12 through which a primary refrigerant flows sequentially, wherein the distance between the discharge port 14c of the primary refrigerant in the compressor 14 and the evaporator 12 is longer than the distance between the discharge port 14c and the condenser 13.

[0111] As a result, the amount of heat, such as radiant heat, transferred from the discharge port 14c of the compressor 14 to the evaporator 12 is less than the amount of radiant heat transferred to the condenser 13.

[0112] (3) The vehicle refrigeration cycle unit 100 according to the third embodiment is a vehicle refrigeration cycle unit 100 interposed between an outdoor heat exchanger 31 and an indoor heat exchanger 21, which exchanges heat between the secondary refrigerants flowing through the outdoor heat exchanger 31 and the indoor heat exchanger 21, and comprises a refrigeration cycle 10 having a compressor 14, a condenser 13, an expansion valve 16, and an evaporator 12 through which a primary refrigerant flows sequentially, wherein the length of the piping connecting the compressor 14 and the evaporator 12 is longer than the length of the piping connecting the compressor 14 and the condenser 13.

[0113] This makes it more difficult for heat to transfer from the compressor 14 to the evaporator 12 through these pipes.

[0114] (4) The vehicle refrigeration cycle unit 100 according to the fourth embodiment is any of the vehicle refrigeration cycle units 100 of (1) to (3), wherein the condenser 13 may be arranged between the compressor 14 and the evaporator 12.

[0115] As a result, the amount of heat, such as radiant heat, transferred from the compressor 14 to the evaporator 12 is less than the amount of heat transferred to the condenser 13.

[0116] (5) The vehicle refrigeration cycle unit 100 according to the fifth embodiment is any of the vehicle refrigeration cycle unit 100 of (1) to (3), which may further include a partition wall portion 17 between the condenser 13 and the evaporator 12 that separates the condenser 13 and the evaporator 12.

[0117] This allows the partition wall 17 to suppress heat transfer from the condenser 13 to the evaporator 12.

[0118] (6) The vehicle refrigeration cycle unit 100 according to the sixth embodiment is the vehicle refrigeration cycle unit 100 of (5), wherein the partition wall portion 17 may have a partition wall plate 17a which is a plate member.

[0119] This makes it possible to suppress heat transfer from the condenser 13 to the evaporator 12 with a simple configuration using plate members.

[0120] (7) The vehicle refrigeration cycle unit 100 according to the seventh embodiment is the vehicle refrigeration cycle unit 100 of (5), wherein the partition wall 17 may have a housing 17b that houses only the compressor 14 and the condenser 13 among the compressor 14, the condenser 13 and the evaporator 12.

[0121] This allows heat such as radiant heat generated from the compressor 14 and condenser 13 to be retained within the housing 17b.

[0122] (8) The vehicle air conditioning system 1 according to the eighth embodiment comprises a vehicle refrigeration cycle unit 100 according to any of (1) to (7), the exterior heat exchanger 31 and the interior heat exchanger 21. [Industrial applicability]

[0123] According to this disclosure, it is possible to provide a vehicle refrigeration cycle unit and a vehicle air conditioning system that can suppress a decrease in the heat exchange efficiency of the evaporator. [Explanation of Symbols]

[0124] 1...Vehicle air conditioning system 10...Refrigeration cycle 11...Casing 11a...Bottom 12...Evaporator 12a,13a...Primary refrigerant inlet 12b,13b...Primary refrigerant outlet 12c,13c...Secondary refrigerant inlet 12d,13d...Secondary refrigerant outlet 13...Condenser 14...Compressor 14a...Compressor casing 14b...Inlet 14c...Outlet 15...Receiver 16...Expansion valve 17...Partition 17a...Partition plate 17b...Housing 20...In-vehicle heat transfer fluid circuit 20a...First heat transfer fluid line 20b...Second heat transfer fluid line 20c...Third heat transfer fluid line 20d...Fourth heat transfer fluid line 20e...Fifth heat transfer fluid line 20f...Sixth heat transfer fluid line 20g...Seventh heat transfer fluid line 21...In-vehicle heat exchanger 21a...Heater core 21b…Cooler core 22…First pump 23…First valve 24…Second valve 30…Exterior heat transfer fluid circuit 30a…Eighth heat transfer fluid line 30b…Ninth heat transfer fluid line 30c…Tenth heat transfer fluid line 30d…Eleventh heat transfer fluid line 30e…Twelfth heat transfer fluid line 30f…First connection line 30g…Second connection line 30h…Third connection line 30i…Fourth connection line 31…Exterior heat exchanger 32…Second pump 33…Third valve 34…Fourth valve 35…Fifth valve 36…Battery cooler 100…Vehicle refrigeration cycle unit 124…Intake line 135…First line 136…Pre-expansion line 143…Discharge line 156…Second line 162…Post-expansion line B…Blower C…Vehicle body F…Front grille G…Direction of gravity H1…First adjacent direction H2…Second adjacent direction

Claims

1. A vehicle refrigeration cycle unit that performs heat exchange between a secondary refrigerant flowing through an external heat transfer medium circuit having an external heat exchanger and an internal heat transfer medium circuit having an internal heat exchanger, The system includes a refrigeration cycle comprising a compressor, condenser, expansion valve, and evaporator through which the primary refrigerant flows sequentially. During heating operation, the condenser exchanges heat between the secondary refrigerant flowing through the in-vehicle heat transfer medium circuit and the primary refrigerant, and the evaporator exchanges heat between the secondary refrigerant flowing through the out-vehicle heat transfer medium circuit and the primary refrigerant. During cooling operation, the condenser exchanges heat between the secondary refrigerant flowing through the external heat transfer medium circuit and the primary refrigerant, and the evaporator exchanges heat between the secondary refrigerant flowing through the internal heat transfer medium circuit and the primary refrigerant. A vehicle refrigeration cycle unit in which the distance between the compressor and the evaporator is longer than the distance between the compressor and the condenser.

2. The vehicle refrigeration cycle unit according to claim 1, wherein the condenser is positioned between the compressor and the evaporator.

3. A partition wall is further provided between the condenser and the evaporator, separating the condenser and the evaporator. The vehicle refrigeration cycle unit according to claim 1, wherein the partition wall portion has a partition plate which is a plate member.

4. A partition wall is further provided between the condenser and the evaporator, separating the condenser and the evaporator. The vehicle refrigeration cycle unit according to claim 1, wherein the partition wall portion has a housing that accommodates only the compressor and the condenser among the compressor, the condenser and the evaporator, thereby suppressing the transfer of heat from the compressor and the condenser to the evaporator.

5. The condenser and the evaporator are further provided with a partition wall separating the condenser and the evaporator, The vehicle refrigeration cycle unit according to claim 1, wherein the partition wall extends between the expansion valve and the evaporator, thereby separating the expansion valve and the evaporator.

6. A vehicle refrigeration cycle unit according to any one of claims 1 to 5, The aforementioned external heat transfer circuit and the internal heat transfer circuit, A vehicle air conditioning system equipped with the following features.

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