Refrigeration cycle device

Abstract

The refrigeration cycle device includes: a receiver section (15) for gas-liquid separation of refrigerant flowing out from the receiver-side pressure reducing section (23a, 23b) and storage of remaining refrigerant; and a refrigerant circuit switching section (14a-14d). The refrigerant circuit switching section (14a-14d) switches between a first flow path and a second flow path. The first flow path allows refrigerant flowing out from the outdoor heat exchange section (18) to flow into the receiver-side pressure reducing section (23a, 23b), and allows refrigerant flowing out from the receiver section (15) to be depressurized by the evaporator-side pressure reducing section (16b, 16c) and flow into the evaporator section (19, 20). The second flow path allows refrigerant flowing out from the heat dissipation section (12) to flow into the receiver-side pressure reducing section (23a, 23b), and allows refrigerant flowing out from the receiver section (15) to be depressurized by the evaporator-side pressure reducing section (16b, 16c) and flow into the evaporator section (19, 20). It also includes a deceleration unit (33, 34) that reduces the flow rate of refrigerant flowing into the receiver section (15).

Description

[0001] Cross-reference of related applications

[0002] This application is based on Japanese Patent Application No. 2020-112803, filed on June 30, 2020, the contents of which are incorporated herein by reference. Technical Field

[0003] The present invention relates to a refrigeration cycle apparatus having a receiver section for storing the remaining refrigerant in the cycle. Background Technology

[0004] Previously, Patent Document 1 disclosed a vapor compression type refrigeration cycle device for use in electric vehicles, etc. The refrigeration cycle device of Patent Document 1 is configured to switch the refrigerant circuit according to the operating mode. For example, in the refrigeration cycle device of Patent Document 1, a refrigerant circuit can switch between a heating mode for heating the vehicle interior, a cooling mode for cooling the vehicle interior, and a cooling mode for cooling the battery, etc.

[0005] As described in Patent Document 1, in a refrigeration cycle apparatus that switches the refrigerant circuit according to an operating mode, the necessary refrigerant flow rate for circulation according to the operating mode can easily change. To address this, the refrigeration cycle apparatus of Patent Document 1 includes a receiver unit that allows refrigerant to circulate at an appropriate flow rate corresponding to the operating mode. The receiver unit separates the refrigerant into gas and liquid phases and stores a portion of the separated liquid refrigerant as surplus refrigerant.

[0006] Existing technical documents

[0007] Patent documents

[0008] Patent Document 1: International Publication No. 2012 / 114439

[0009] However, in refrigeration cycle devices where the refrigerant flow rate varies depending on the operating mode, the receiver section needs to perform its gas-liquid separation function effectively during the operating mode with the highest refrigerant flow rate. This is because, in the operating mode with the highest refrigerant flow rate, the remaining refrigerant stored in the receiver section becomes minimal. Therefore, the possibility of the separated gaseous refrigerant remixing with the liquid refrigerant, becoming a gas-liquid mixture, and flowing out of the receiver section increases.

[0010] In response to this, in operating modes with a higher refrigerant flow rate, techniques have been considered to increase the amount of refrigerant injected into the circulation to ensure that the receiver section can perform its gas-liquid separation function effectively. However, as described in Patent Document 1, in refrigeration cycle devices capable of switching between various operating modes, the difference between the remaining refrigerant charge in operating modes with a higher refrigerant flow rate and those with a lower refrigerant flow rate tends to widen.

[0011] Therefore, if the refrigerant charge is increased to ensure sufficient gas-liquid separation performance of the receiver section in operating modes with higher refrigerant flow rates, the receiver section must be enlarged to store excess refrigerant in operating modes with lower refrigerant flow rates. However, this enlargement of the receiver section leads to a deterioration in the overall refrigeration cycle system's usability and productivity. Summary of the Invention

[0012] The present invention was made in view of the above-mentioned problems, and its object is to provide a refrigeration cycle apparatus configured to switch the refrigerant circuit and to suppress the enlargement of the receiver section.

[0013] To achieve the above objectives, the refrigeration cycle apparatus of the first aspect of the present invention includes a compressor, a heat dissipation unit, an outdoor heat exchange unit, a receiver-side pressure reducing unit, a receiver unit, an evaporator-side pressure reducing unit, an evaporator unit, and a refrigerant circuit switching unit.

[0014] The compressor compresses and discharges the refrigerant. The heat dissipation section dissipates heat from the refrigerant discharged from the compressor. The outdoor heat exchange section allows the refrigerant to exchange heat with the outside air. The receiver-side pressure reducing section reduces the pressure of the refrigerant. The receiver section performs gas-liquid separation on the refrigerant flowing out from the receiver-side pressure reducing section and stores the remaining refrigerant in the cycle. The evaporator-side pressure reducing section reduces the pressure of the refrigerant. The evaporator section evaporates the refrigerant that has been pressure-reduced by the evaporator-side pressure reducing section.

[0015] The refrigerant circuit switching unit switches the refrigerant circuit. The refrigerant circuit switching unit can switch to a first circuit, which allows refrigerant flowing from the outdoor heat exchange section to flow into the receiver-side pressure reducing section, refrigerant flowing from the receiver section to flow into the evaporator-side pressure reducing section, and refrigerant depressurized by the evaporator-side pressure reducing section to flow into the evaporator. The refrigerant circuit switching unit can also switch to a second circuit, which allows refrigerant flowing from the heat dissipation section to flow into the receiver-side pressure reducing section, refrigerant flowing from the receiver section to flow into the evaporator-side pressure reducing section, and refrigerant depressurized by the evaporator-side pressure reducing section to flow into the evaporator.

[0016] The refrigeration cycle unit also includes a deceleration section. The deceleration section reduces the flow rate of the refrigerant flowing into the receiver section after being depressurized by the pressure reducing section on the receiver side.

[0017] Therefore, since it has a refrigerant circuit switching unit, the refrigerant circuit can be switched. In addition, since it has a receiver unit, the operating mode can be switched by switching the refrigerant circuit, and even if the circulating refrigerant flow rate changes, the remaining circulating refrigerant can be stored in the receiver unit.

[0018] Because it also has a deceleration section, even when switching to an operating mode where the refrigerant flow rate increases and the remaining refrigerant charge in the receiver section decreases, the gas-liquid separation performance of the receiver section can be suppressed.

[0019] More specifically, in the operating mode where the refrigerant flow rate increases, not only does the remaining refrigerant charge in the receiver section decrease, but the flow rate of the refrigerant flowing into the receiver section through the deceleration section also increases. Because of the deceleration section, the flow rate of the refrigerant flowing into the receiver section can be reduced. Therefore, the reduction in the gas-liquid separation performance of the receiver section can be suppressed.

[0020] As a result, in operating modes with a low remaining refrigerant charge, the increase in the amount of refrigerant required to ensure adequate gas-liquid separation performance of the receiver section can be minimized. In other words, even when configured to switch refrigerant circuits, the size of the receiver section can be prevented from increasing according to the refrigeration cycle device of the first embodiment. Attached Figure Description

[0021] Figure 1 This is an overall structural diagram of the refrigeration cycle device according to the first embodiment.

[0022] Figure 2 This is a perspective view of the receiver assembly according to the first embodiment.

[0023] Figure 3 From Figure 2 A perspective view of the receiver assembly as observed from the back side of the paper.

[0024] Figure 4 This is a schematic cross-sectional view showing the collision plate of the receiver assembly in the first embodiment.

[0025] Figure 5 yes Figure 4 VV sectional view.

[0026] Figure 6 This is a schematic structural diagram of the indoor air conditioning unit according to the first embodiment.

[0027] Figure 7 This is a block diagram showing the electrical control section of the vehicle air conditioning unit according to the first embodiment.

[0028] Figure 8 This is a schematic cross-sectional view showing a modified example of the collision plate of the receiver assembly in the first embodiment.

[0029] Figure 9 This is a schematic cross-sectional view showing another variation of the collision plate of the receiver assembly in the first embodiment.

[0030] Figure 10 This is a schematic cross-sectional view showing the refrigerant passage for deceleration in the receiver assembly of the second embodiment.

[0031] Figure 11 This is a schematic cross-sectional view showing the refrigerant passage for deceleration in the receiver assembly of the third embodiment.

[0032] Figure 12 This is a schematic cross-sectional view showing the refrigerant passage for deceleration in the receiver assembly of the fourth embodiment.

[0033] Figure 13 This is an overall structural diagram of the refrigeration cycle device according to the fifth embodiment.

[0034] Figure 14 This is an overall structural diagram of the refrigeration cycle device according to the sixth embodiment.

[0035] Figure 15 This is a schematic cross-sectional view illustrating a receiver assembly in another embodiment.

[0036] Figure 16 This is a schematic cross-sectional view illustrating another receiver component in other embodiments.

[0037] Figure 17 This is a schematic cross-sectional view illustrating yet another receiver assembly in other embodiments. Detailed Implementation

[0038] Hereinafter, several embodiments for carrying out the present invention will be described with reference to the accompanying drawings. In each embodiment, the same reference numerals are sometimes used to denote parts corresponding to matters described in previous embodiments, and repeated descriptions are omitted. Where only a part of the structure is described in each embodiment, other embodiments described above can be applied to other parts of the structure. Not only can the parts that are specifically and explicitly shown to be combinable in each embodiment be combined with each other, but embodiments can also be partially combined with each other even if not explicitly stated, provided there are no particular obstacles to the combination.

[0039] (First Implementation)

[0040] use Figures 1 to 7This section describes a first embodiment of the refrigeration cycle device 10 according to the present invention. The refrigeration cycle device 10 is applied to a vehicle air conditioning system installed in an electric vehicle. An electric vehicle is a vehicle that obtains driving force for driving from an electric motor. The vehicle air conditioning system of this embodiment is an air conditioning system with onboard equipment cooling function, which regulates the air in the vehicle interior, which is the space to be conditioned, and cools the battery 80, which is an onboard device, in the electric vehicle.

[0041] Battery 80 stores the power supplied to vehicle-mounted equipment such as electric motors. Battery 80 is a secondary battery (in this embodiment, a lithium-ion battery). Battery 80 is a battery pack formed by stacking multiple battery cells and connecting these battery cells in series or parallel.

[0042] This type of battery generates heat during operation (i.e., during charging and discharging). The battery's output tends to decrease at low temperatures and deteriorates easily at high temperatures. Therefore, the battery temperature needs to be maintained within a suitable temperature range (15°C or higher and 55°C or lower in this embodiment). Therefore, in the vehicle air conditioning system of this embodiment, the battery 80 is cooled using the cold energy generated by the refrigeration cycle device 10.

[0043] In a vehicle air conditioning system, the refrigeration cycle unit 10 adjusts the temperature of the air blown into the vehicle interior. Furthermore, the refrigeration cycle unit 10 generates heat to cool the battery 80. Therefore, the refrigeration cycle unit 10 adjusts the temperature of both the air and the battery 80. Additionally, the refrigeration cycle unit 10 is configured to switch the refrigerant circuit according to various operating modes used for air conditioning of the vehicle interior and cooling of the battery 80.

[0044] In the refrigeration cycle unit 10, an HFO-based refrigerant (specifically R1234yf) is used as the refrigerant. The refrigeration cycle unit 10 constitutes a vapor compression subcritical refrigeration cycle in which the pressure of the high-pressure refrigerant discharged from the compressor 11 does not exceed the critical pressure of the refrigerant. Refrigeration oil (specifically PAG oil) for lubricating the compressor 11 is mixed into the refrigerant. A portion of the refrigeration oil circulates in the cycle along with the refrigerant.

[0045] In the refrigeration cycle unit 10, the compressor 11 draws in, compresses, and discharges refrigerant. The compressor 11 is disposed in the drive unit compartment on the front side of the vehicle compartment. The drive unit compartment forms a space for accommodating at least a portion of a drive device (e.g., an electric motor) for outputting driving force for travel.

[0046] The compressor 11 is an electric compressor with a fixed capacity type, driven by an electric motor to rotate a compressor mechanism with a fixed discharge capacity. The speed (i.e., refrigerant discharge capacity) of the compressor 11 is controlled according to a control signal output from the control device 70 described later.

[0047] The outlet of compressor 11 is connected to the inlet side of the refrigerant passage of water refrigerant heat exchanger 12. Water refrigerant heat exchanger 12 has a refrigerant passage for the high-pressure refrigerant discharged from compressor 11 and a water passage for the high-temperature side heat medium circulating in the high-temperature side heat medium circuit 50. Water refrigerant heat exchanger 12 is a heat dissipation section that allows heat exchange between the high-pressure refrigerant flowing in the refrigerant passage and the high-temperature side heat medium flowing in the water passage, thereby dissipating heat from the high-pressure refrigerant to the high-temperature side heat medium. The high-temperature side heat medium circuit 50 will be described later.

[0048] The outlet of the refrigerant passage of the water refrigerant heat exchanger 12 is connected to the first inlet 31a side of the receiver assembly 30. The receiver assembly 30 is for... Figure 1 The constituent devices enclosed by dashed lines, such as Figure 2 , Figure 3 The components appear as integrated as shown in the 3D view.

[0049] Specifically, the receiver assembly 30 is an integrated assembly that includes the first on / off valve 14a to the third on / off valve 14c, the receiver part 15, the heating expansion valve 16a, the first check valve 17a, the second check valve 17b, the heating fixed throttling component 23a, the cooling fixed throttling component 23b, and the collision plate 33.

[0050] First, the constituent devices constituting the receiver assembly 30 will be described. The first inlet 31a of the receiver assembly 30 is connected to the inlet side of the first internal tee connector 13a formed within the receiver assembly 30. The first internal tee connector 13a has three inlet and outlet ports that communicate with each other. The first internal tee connector 13a is formed by providing multiple refrigerant passages in a metal block forming the receiver assembly 30.

[0051] Furthermore, as described later, a second internal tee connector 13b to a fourth internal tee connector 13d are formed within the receiver assembly 30. The basic structure of the second internal tee connector 13b to the fourth internal tee connector 13d is the same as that of the first internal tee connector 13a.

[0052] When the first internal tee connector 13a to the fourth internal tee connector 13d uses one of the three inlet outlets as the inlet and two as the outlets, it becomes a branch section that branches the flow of refrigerant flowing in from one inlet. Furthermore, when two of the three inlet outlets are used as inlets and one as the outlet, it becomes a confluence section that merges the flow of refrigerant flowing in from the two inlets.

[0053] One outlet of the first internal tee connector 13a is connected to the inlet side of the receiver section 15 via the first on / off valve 14a, the heating fixed throttling component 23a, and the third internal tee connector 13c. The other outlet of the first internal tee connector 13a is connected to the inlet side of the heating expansion valve 16a via the second on / off valve 14b and the second internal tee connector 13b.

[0054] The first on / off valve 14a is a solenoid valve that opens and closes the inlet-side passage 21a from one outlet of the first internal three-way connector 13a to the inlet of the receiver section 15. The opening and closing action of the first on / off valve 14a is controlled by a control voltage output from the control device 70. Furthermore, as described later, the receiver assembly 30 includes a third on / off valve 14c. The basic structure of the second on / off valve 14b and the third on / off valve 14c is the same as that of the first on / off valve 14a.

[0055] The heating-type fixed throttling component 23a is a receiver-side pressure-reducing section that reduces the pressure of the refrigerant flowing into the receiver section 15. The heating-type fixed throttling component 23a can be a throttling orifice, a capillary tube, or the like. As described later, the receiver assembly 30 also includes a cooling-type fixed throttling component 23b, which serves as a receiver-side pressure-reducing section. The basic structure of the cooling-type fixed throttling component 23b is the same as that of the heating-type fixed throttling component 23a.

[0056] In the inlet-side passage 21a, one inlet of the third internal tee connector 13c is connected to the outlet side of the heating fixed throttling component 23a. In the inlet-side passage 21a, the outlet of the third internal tee connector 13c is connected to the inlet side of the receiver section 15. The other inlet of the third internal tee connector 13c is connected to the second inlet 32a side of the receiver assembly 30 via the refrigeration fixed throttling component 23b and the first check valve 17a.

[0057] The first check valve 17a allows refrigerant to flow from the second inlet 32a side of the receiver assembly 30 to the third internal tee 13c side, and prevents refrigerant from flowing from the third internal tee 13c side to the second inlet 32a side.

[0058] The receiver section 15 is a bottomed cylindrical metal container with gas-liquid separation function. In the refrigeration cycle device 10, the receiver section 15 performs gas-liquid separation on the refrigerant flowing out from the heat exchange section, which functions as a condenser for condensing the refrigerant. Furthermore, the receiver section 15 is a liquid storage section that allows a portion of the separated liquid refrigerant to flow downstream and stores the remaining liquid refrigerant as surplus refrigerant within the cycle.

[0059] like Figure 4As shown, a generally cylindrical internal space 15a extending vertically is formed inside the receiver section 15. An inlet pipe 15b, an outlet pipe 15c, and a collision plate 33 are disposed within the internal space 15a. Furthermore, in... Figure 4 In the diagram, dotted shading lines indicate areas where liquid refrigerant is stored. This is shown in the following diagram. Figure 8 The same applies to the following.

[0060] The inlet pipe 15b is a metal pipe that allows refrigerant, after being depressurized by the fixed throttling component 23a for heating or cooling, to flow into the internal space 15a of the receiver section 15. Therefore, the inlet pipe 15b forms the downstream portion of the inlet-side passage 21a. The refrigerant outlet of the inlet pipe 15b allows the refrigerant to flow out towards the collision portion 33a of the collision plate 33.

[0061] The collision plate 33 is a deceleration unit that reduces the flow rate of refrigerant flowing into the internal space 15a of the receiver section 15. For example... Figure 4 , Figure 5 As shown, the collision plate 33 is a metal plate-shaped component arranged in a horizontally extending manner within the internal space 15a. The collision plate 33 has a collision portion 33a and a connecting portion 33b.

[0062] The collision section 33a is the part that collides with the refrigerant flowing into the receiver section 15. The refrigerant flowing into the receiver section 15 has its flow rate reduced due to the collision with the collision section 33a. Therefore, the refrigerant outlet of the inlet pipe 15b opens directly above the collision section 33a, so that the refrigerant flowing out of the inlet pipe 15b will definitely collide with the collision section 33a.

[0063] The connecting portion 33b is a section in which multiple through holes 33c are formed, penetrating both the surface and interior of the collision plate 33. The heavier liquid refrigerant, whose flow rate decreases upon colliding with the collision portion 33a, falls through the through holes 33c into the lower side of the internal space 15a of the receiver portion 15. The connecting portion 33b can be formed, for example, by stamping a plate-shaped component.

[0064] like Figure 5 As shown, in the region where the connecting portion 33b is formed in the collision plate 33, a plurality of through holes 33c are arranged in a circular shape at approximately equal angular intervals around the central axis of the receiver portion 15. Of course, the through holes 33c are not formed in the region where the collision portion 33a is formed in the collision plate 33. All the through holes 33c are formed in a circular shape with the same diameter (1 mm in this embodiment).

[0065] As described above, the through-hole 33c is a hole used to allow the liquid refrigerant, whose flow rate is reduced due to collision with the collision section 33a, to fall towards the lower side of the internal space 15a. Therefore, with the total opening area SA(m²) of the through-hole 33c...2 As the number of through holes increases, the refrigerant flow rate through the through holes 33c decreases. The total opening area SA can be calculated by accumulating the opening areas of each through hole 33c and the number of through holes 33c N.

[0066] Furthermore, by reducing the flow rate of the refrigerant through the through-hole 33c, foaming (so-called bubbling) of the liquid refrigerant accumulated on the lower side of the internal space 15a of the receiver section 15 can be suppressed. Bubbling is the cause of the gas-liquid mixed refrigerant flowing out of the receiver section 15. Therefore, suppressing bubbling is effective in suppressing the decrease in the coefficient of performance (COP) of the refrigeration cycle device 10.

[0067] Therefore, in this embodiment, the number N of through holes 33c and the total opening area SA are determined in such a way that the dimensionless parameter P1 defined by the following formula F1 satisfies the following formula F2.

[0068] P1=(Gr / N) / (ρ×V0×R0 2 )×(Gr / SA / ρ) / V0…(F1)

[0069] P1≤0.435…(F2)

[0070] Additionally, Gr is the refrigerant flow rate (mass flow rate: kg / s) flowing through the receiver section 15. ρ is the density of the liquid refrigerant (kg / m³). 3 V0 is the refrigerant velocity (m / s) flowing through outlet pipe 15c. R0 is the equivalent diameter (m) of outlet pipe 15c.

[0071] That is, the dimensionless parameter P1, represented by the formula F1, is a dimensionless parameter that takes into account the flow rate of the refrigerant flowing out of the outlet pipe 15c and gives the amount of motion to the liquid surface of the liquid refrigerant stored in the receiver section 15 by the refrigerant passing through a through hole 33c.

[0072] Therefore, as the dimensionless parameter P1 decreases, the amount of motion imparted to the liquid surface also decreases. In other words, as the dimensionless parameter P1 decreases, it is easier to suppress the foaming of the liquid refrigerant accumulated in the internal space 15a of the receiver section 15. In addition, formula F2 represents the range within which the enlargement of the receiver section 15 can be suppressed, taking into account the diameter and spacing of the through holes 33c that can actually be formed in the collision plate 33.

[0073] The collision plate 33 is fixed inside the internal space 15a of the receiver section 15. The collision plate 33 is disposed on the upper side of the center portion of the internal space 15a of the receiver section 15 in the vertical direction.

[0074] The outlet pipe 15c is a circular metal pipe that allows the separated liquid refrigerant to flow out from the internal space 15a of the receiver. The outlet pipe 15c forms the uppermost part of the outlet-side passage 21b, which will be described later. The outlet pipe 15c extends vertically through the collision plate 33. The refrigerant inlet of the outlet pipe 15c opens to the lower side of the receiver section 15, and is located lower than the liquid level of the liquid refrigerant in the operating mode when the remaining refrigerant stored in the receiver section is minimal.

[0075] Next, as Figure 1 As shown, the second on / off valve 14b is a solenoid valve that opens and closes the outdoor unit side passage 21c from the outlet of the first internal tee connector 13a to the first outlet 31b of the receiver assembly 30.

[0076] The inlet of the other side of the second internal tee connector 13b is connected to the outlet side of the receiver section 15. In the outlet side passage 21b from the outlet of the receiver section 15 to the inlet of the other side of the second internal tee connector 13b, a fourth internal tee connector 13d, a third on / off valve 14c and a second check valve 17b are arranged sequentially from the outlet side of the receiver section 15.

[0077] In the outlet-side passage 21b, the inlet of the fourth internal tee connector 13d is connected to the refrigerant outlet side of the receiver section 15. In the outlet-side passage 21b, one outlet of the fourth internal tee connector 13d is connected to the inlet side of the third on / off valve 14c. Furthermore, the other outlet of the fourth internal tee connector 13d is connected to the second outlet 32b side of the receiver assembly 30.

[0078] The third on / off valve 14c is a solenoid valve that opens and closes the outlet side passage 21b. The second check valve 17b allows refrigerant to flow from the third on / off valve 14c side to the second internal tee joint 13b side, and prohibits refrigerant from flowing from the second internal tee joint 13b side to the third on / off valve 14c side.

[0079] The expansion valve 16a for heating is an outdoor unit-side pressure reducing unit that reduces the pressure of the refrigerant flowing out of the receiver section 15 and adjusts the flow rate of the refrigerant flowing downstream when the refrigerant circuit is switched to the outdoor gas heating mode described later.

[0080] The heating expansion valve 16a is an electrically operated variable throttling mechanism having a valve core configured to change the throttling opening and an electric actuator (specifically a stepper motor) that displaces the valve core. The operation of the heating expansion valve 16a is controlled by a control signal (specifically a control pulse) output from the control device 70.

[0081] The expansion valve 16a for heating has a fully open function and a fully closed function. The fully open function is to set the valve opening to be fully open, so it hardly plays a role in flow regulation and refrigerant pressure reduction, and only functions as a refrigerant passage. The fully closed function is to set the valve opening to be fully closed, so as to close the refrigerant passage.

[0082] As described later, the refrigeration cycle device 10 also includes a refrigeration expansion valve 16b and a cooling expansion valve 16c. The basic structure of the refrigeration expansion valve 16b and the cooling expansion valve 16c is the same as that of the heating expansion valve 16a. In addition, the refrigeration expansion valve 16b and the cooling expansion valve 16c in this embodiment are not integrated into the receiver assembly 30, but they can also be integrated into the receiver assembly 30.

[0083] Next, the integration of the constituent devices constituting the receiver assembly 30 will be described. For example... Figures 1-3 As shown, the receiver assembly 30 is generally divided into a switching block 31, a pressure reducing block 32, and a receiver section 15. The switching block 31, the pressure reducing block 32, and the receiver section 15 are formed from different components and are assembled into one unit by means of sealing components, bolt fastening, etc.

[0084] The switching unit block 31 is formed from a block of metal. The switching unit block 31 is formed within the receiver assembly 30. Figure 1 The area enclosed by a single-dot dashed line. A first inlet 31a and a first outlet 31b are formed in the switching section block 31. Multiple refrigerant passages, a first internal tee connector 13a, and a second internal tee connector 13b are formed inside the switching section block 31.

[0085] The switching section block 31 is equipped with a first on / off valve 14a to a third on / off valve 14c and a heating expansion valve 16a. A second check valve 17b is provided in the refrigerant passage formed in the switching section block 31.

[0086] The pressure-reducing block 32 is formed from a block of metal. The pressure-reducing block 32 is formed within the receiver assembly 30. Figure 1 The area enclosed by the double-dotted line. A second inlet 32a and a second outlet 32b are formed in the pressure-reducing section using block 32. Multiple refrigerant passages, a third internal tee connector 13c, and a fourth internal tee connector 13d are formed inside the pressure-reducing section using block 32.

[0087] A first check valve 17a, a heating fixed throttling component 23a, and a cooling fixed throttling component 23b are provided in the refrigerant passage formed in the pressure reducing block 32.

[0088] In the receiver assembly 30, the switching block 31 and the pressure reducing block 32 are integrated in a manner that allows them to contact each other via a sealing member or the like. Furthermore, the pressure reducing block 32 and the receiver unit 15 are integrated in a manner that allows them to contact each other via a sealing member or the like. Moreover, in the receiver assembly 30, the switching block 31 and the receiver unit 15 are integrated in a non-contact manner, without contact between them.

[0089] like Figure 1 As shown, the first outlet 31b of the receiver assembly 30 is connected to the refrigerant inlet side of the outdoor heat exchanger 18. The outdoor heat exchanger 18 is an outdoor heat exchange section that allows the refrigerant flowing out from the heating expansion valve 16a to exchange heat with the outside air blown by an outside air fan (not shown). The outdoor heat exchanger 18 is located on the front side of the drive unit compartment. Therefore, when the vehicle is in motion, the driving air can come into contact with the outdoor heat exchanger 18.

[0090] The refrigerant outlet of the outdoor heat exchanger 18 is connected to the inlet side of the first external tee joint 13e. The first external tee joint 13e is formed by a piping fitting having three inlet and outlet ports that are interconnected.

[0091] Furthermore, as described later, the refrigeration cycle device 10 includes a second external tee connector 13f. The basic structure of the second external tee connector 13f is the same as that of the first external tee connector 13e. The basic functions of the first external tee connector 13e and the second external tee connector 13f are the same as those of the first internal tee connectors 13a to the fourth internal tee connectors 13d of the receiver assembly 30.

[0092] One outlet of the first external tee 13e is connected to the second inlet 32a side of the receiver assembly 30. The other outlet of the first external tee 13e is connected to one inlet side of the four-way connector 13g via the fourth on / off valve 14d and the third check valve 17c.

[0093] The fourth on / off valve 14d is a solenoid valve that opens and closes the suction-side passage 21d from the outlet of the first external tee 13e to one inlet of the four-way connector 13g. The third check valve 17c allows refrigerant to flow from the third on / off valve 14c side to the four-way connector 13g side, and prevents refrigerant from flowing from the four-way connector 13g side to the third on / off valve 14c side. The four-way connector 13g is formed by a piping fitting having four interconnected inlet and outlet ports. Of course, the four-way connector 13g can also be a component formed by combining two tee connectors.

[0094] The second outlet 32b of the receiver assembly 30 is connected to the inlet side of the second external tee connector 13f. One outlet of the second external tee connector 13f is connected to the inlet side of the refrigeration expansion valve 16b. The other outlet of the second external tee connector 13f is connected to the inlet side of the cooling expansion valve 16c.

[0095] When the refrigerant circuit, etc., is switched to the refrigeration mode described later, the refrigeration expansion valve 16b depressurizes the refrigerant flowing out of the receiver section 15 and adjusts the flow rate of the refrigerant flowing downstream. Therefore, the evaporator-side pressure reducing section includes the refrigeration expansion valve 16b.

[0096] The outlet of the expansion valve 16b is connected to the refrigerant inlet side of the indoor evaporator 19. The indoor evaporator 19 is disposed within the housing 41 of the indoor air conditioning unit 40. The indoor evaporator 19 evaporates the low-pressure refrigerant, which has been depressurized by the expansion valve 16b, by exchanging heat with the supply air blown from the indoor fan 42. Therefore, the evaporation section includes the indoor evaporator 19.

[0097] In other words, the indoor evaporator 19 is a cooling section for the supply air that cools the supply air by absorbing heat through the evaporation of low-pressure refrigerant. The refrigerant outlet of the indoor evaporator 19 is connected to the other inlet side of the four-way connector 13g via a fourth check valve 17d. The fourth check valve 17d allows refrigerant to flow from the indoor evaporator 19 side to the four-way connector 13g side, and prevents refrigerant from flowing from the four-way connector 13g side to the indoor evaporator 19 side.

[0098] When switching to the refrigerant circuit in the cooling mode described later, the cooling expansion valve 16c depressurizes the refrigerant flowing out of the receiver section 15 and adjusts the flow rate of the refrigerant flowing downstream. Therefore, the evaporator-side depressurization section includes the cooling expansion valve 16c.

[0099] The outlet of the cooling expansion valve 16c is connected to the refrigerant inlet side of the chiller 20. The chiller 20 has a refrigerant passage and a water passage. The refrigerant passage is for the flow of low-pressure refrigerant that has been depressurized by the cooling expansion valve 16c, and the water passage is for the flow of the low-temperature side heat medium circulating in the low-temperature side heat medium circuit 60. The chiller 20 evaporates the low-pressure refrigerant by exchanging heat between the low-pressure refrigerant flowing in the refrigerant passage and the low-temperature side heat medium flowing in the water passage. Therefore, the evaporation section includes the chiller 20.

[0100] In other words, the chiller 20 is a cooling section for the low-temperature side heat medium, which cools the heat medium by absorbing heat through the evaporation of low-pressure refrigerant. The refrigerant outlet of the chiller 20 is connected to another inlet side of the four-way connector 13g. The outlet of the four-way connector 13g is connected to the suction inlet side of the compressor.

[0101] As explained above, in the refrigeration cycle device 10, the refrigerant circuit can be switched by opening and closing the refrigerant passage through the first on / off valve 14a to the third on / off valve 14c and the fourth on / off valve 14d of the receiver assembly 30. Therefore, the refrigerant circuit switching unit includes the first on / off valve 14a to the fourth on / off valve 14d.

[0102] Furthermore, the heating expansion valve 16a, the cooling expansion valve 16b, and the cooling expansion valve 16c can switch the refrigerant circuit by performing the aforementioned fully closed function. That is, the heating expansion valve 16a, the cooling expansion valve 16b, and the cooling expansion valve 16c also function as refrigerant circuit switching units.

[0103] Of course, a variable throttling mechanism without a fully closed function can also be combined with an on / off valve to form a heating expansion valve 16a, a cooling expansion valve 16b, and a cooling expansion valve 16c. In this case, the on / off valve is a refrigerant circuit switching unit.

[0104] Next, the high-temperature side heat medium circuit 50 will be described. Figure 1 The high-temperature side heat medium circuit 50 shown is a heat medium circulation circuit for circulating high-temperature side heat medium. Ethylene glycol aqueous solution is used as the high-temperature side heat medium. The high-temperature side heat medium circuit 50 is equipped with a water passage of water refrigerant heat exchanger 12, a high-temperature side heat medium pump 51, a heater core 52, etc.

[0105] The high-temperature side heat medium pump 51 is a liquid pump that pressurizes the high-temperature side heat medium to the inlet side of the water passage of the water refrigerant heat exchanger 12. The high-temperature side heat medium pump 51 is an electric pump whose speed (i.e., pressing capacity) is controlled according to the control voltage output from the control device 70.

[0106] The outlet of the water passage of the water refrigerant heat exchanger 12 is connected to the heat medium inlet side of the heater core 52. The heater core 52 is a heat exchanger that heats the supply air by exchanging heat between the high-temperature side heat medium heated by the water refrigerant heat exchanger 12 and the supply air passing through the indoor evaporator 19. The heater core 52 is disposed within the housing 41 of the indoor air conditioning unit 40. The heat medium outlet of the heater core 52 is connected to the suction port side of the high-temperature side heat medium pump 51.

[0107] Therefore, in the high-temperature side heat medium circuit 50, the heat dissipation of the high-temperature side heat medium in the heater core 52 to the supply air can be adjusted by adjusting the flow rate of the high-temperature side heat medium flowing into the heater core 52 through the high-temperature side heat medium pump 51. That is, the heating amount of the supply air in the heater core 52 can be adjusted.

[0108] In this embodiment, a heating section is constructed by using the water refrigerant heat exchanger 12 and the high-temperature side heat medium circuit 50 to heat the supply air by using the refrigerant discharged from the compressor 11 as a heat source.

[0109] Next, the low-temperature side heat medium circuit 60 will be described. Figure 1 The low-temperature side heat medium circuit 60 shown is a heat medium circulation circuit for circulating the low-temperature side heat medium. The same fluid as the high-temperature side heat medium is used as the low-temperature side heat medium. The low-temperature side heat medium circuit 60 is equipped with a water passage for the chiller 20, a low-temperature side heat medium pump 61, and a cooling water passage 80a for the battery 80, etc.

[0110] The cryogenic heat transfer medium pump 61 is a liquid pump that pressurizes the cryogenic heat transfer medium to the inlet side of the water passage of the chiller 20. The basic structure of the cryogenic heat transfer medium pump 61 is the same as that of the high-temperature heat transfer medium pump 51. The outlet of the water passage of the chiller 20 is connected to the inlet side of the cooling water passage 80a of the battery 80.

[0111] Cooling water passage 80a is formed inside the battery casing that houses the battery cells of battery 80. Cooling water passage 80a is a passage structure that connects multiple passages in parallel inside the battery casing. Therefore, cooling water passage 80a can evenly cool all battery cells. The outlet of cooling water passage 80a is connected to the suction port of the cryogenic heat transfer medium pump 61.

[0112] In this embodiment, the cooling unit of the cooling battery 80 is constructed by utilizing the chiller 20 and the constituent devices of the low-temperature side heat medium circuit 60 to cool the object to be cooled.

[0113] Next, use Figure 6 The interior air conditioning unit 40 will be described below. In a vehicle air conditioning system, the interior air conditioning unit 40 is a unit used to appropriately blow temperature-adjusted supply air to appropriate parts of the vehicle interior. The interior air conditioning unit 40 is located inside the instrument panel (i.e., instrument panel) at the front of the vehicle interior.

[0114] The indoor air conditioning unit 40 has a housing 41 that forms an air passage for supplying air. An indoor fan 42, an indoor evaporator 19, a heater core 52, etc., are arranged in the air passage formed within the housing 41. The housing 41 is formed of a resin (e.g., polypropylene) that has a certain degree of elasticity and excellent strength.

[0115] An internal / external air switching device 43 is disposed at the upstream side of the airflow in the housing 41. The internal / external air switching device 43 switches the introduction of internal air (indoor air) and external air (outdoor air) into the housing 41. The operation of the electric actuator for driving the internal / external air switching device 43 is controlled according to the control signal output from the control device 70.

[0116] An indoor air supply fan 42 is disposed downstream of the airflow from the indoor / outdoor air switching device 43. The indoor air supply fan 42 blows air drawn in via the indoor / outdoor air switching device 43 into the vehicle interior. The indoor air supply fan 42 is an electric fan driven by a centrifugal multi-bladed fan driven by an electric motor. The speed (i.e., air supply capacity) of the indoor air supply fan 42 is controlled according to the control voltage output from the control device 70.

[0117] Downstream of the supply airflow from the indoor fan 42, an indoor evaporator 19 and a heater core 52 are arranged sequentially relative to the supply airflow. That is, the indoor evaporator 19 is positioned upstream of the supply airflow compared to the heater core 52. Inside the housing 41, a cold air bypass passage 45 is formed, allowing the supply air passing through the indoor evaporator 19 to bypass the heater core 52 and flow downstream.

[0118] An air mixing gate 44 is disposed downstream of the supply airflow of the indoor evaporator 19 and upstream of the supply airflow of the heater core 52. The air mixing gate 44 adjusts the ratio of the airflow through the heater core 52 to the airflow through the cold air bypass passage 45 in the supply air after passing through the indoor evaporator 19. The operation of the electric actuator for driving the air mixing gate is controlled according to the control signal output from the control device 70.

[0119] A mixing space 46 is provided downstream of the airflow from the heater core 52. This mixing space 46 allows the airflow heated by the heater core 52 to mix with the airflow that has passed through the cold air bypass passage 45 and has not been heated by the heater core 52. In addition, at the downstream end of the airflow from the housing 41, an opening (not shown) is provided to blow the airflow (air conditioning air) mixed in the mixing space 46 into the vehicle interior.

[0120] Therefore, by adjusting the airflow ratio between the airflow through the heater core 52 and the airflow through the cold air bypass passage 45 using the air mixing door 44, the temperature of the air conditioning air mixed in the mixing space 46 can be adjusted. Then, the temperature of the supplied air blown into the vehicle interior from each opening can be adjusted.

[0121] The system includes a face opening, a foot opening, and a defrost opening (none shown in the diagram). The face opening directs air conditioning air towards the upper body of the occupants inside the vehicle. The foot opening directs air conditioning air towards the occupants' feet. The defrost opening directs air conditioning air towards the inside of the vehicle's windshield.

[0122] Upstream of these openings, a blowout mode switching door (not shown) is provided. The blowout mode switching door switches the openings from which air conditioning air is blown out by opening and closing each opening. The operation of the electric actuator driving the blowout mode switching door is controlled by a control signal output from the control device 70.

[0123] Next, use Figure 7 The electrical control unit of the vehicle air conditioning system is described in general. The control unit 70 consists of a well-known microcomputer including a CPU, ROM, and RAM, and its peripheral circuitry. The control unit 70 performs various calculations and processes based on the control program stored in the ROM, and controls the operation of various control objects connected to the output side, such as devices 11, 14a-14d, 16a-16c, 42, 43, 44, 51, and 61.

[0124] like Figure 7 As shown, the input side of the control device 70 is connected to various control sensors. These control sensors include an indoor air temperature sensor 71a, an outdoor air temperature sensor 71b, and a solar radiation sensor 71c. Additionally, the control sensors include a high-pressure sensor 71d, an air conditioning fan temperature sensor 71e, an evaporator temperature sensor 71f, an evaporator pressure sensor 71g, an outdoor unit temperature sensor 71h, an outdoor unit pressure sensor 71i, and a battery temperature sensor 71j. Furthermore, the control sensors include a high-temperature side heat transfer medium temperature sensor 71k and a low-temperature side heat transfer medium temperature sensor 71m.

[0125] Interior air temperature sensor 71a is an interior air temperature detection unit that detects the temperature inside the vehicle, i.e., interior air temperature Tr. Outside air temperature sensor 71b is an outside air temperature detection unit that detects the temperature outside the vehicle, i.e., outside air temperature Tam. Solar radiation sensor 71c is a solar radiation detection unit that detects the amount of solar radiation As shining into the vehicle interior.

[0126] The high-pressure sensor 71d is a high-pressure detection unit that detects the pressure of the high-pressure refrigerant discharged from the compressor 11, i.e., the high-pressure pressure Pd. The air conditioning air temperature sensor 71e is an air conditioning air temperature detection unit that detects the temperature TAV of the air blown into the vehicle interior from the mixing space 46.

[0127] The evaporator temperature sensor 71f is an evaporator temperature detection unit that detects the refrigerant evaporation temperature (evaporator temperature) Te in the indoor evaporator 19. In this embodiment, the evaporator temperature sensor 71f specifically detects the temperature of the refrigerant on the outlet side of the indoor evaporator 19.

[0128] The evaporator pressure sensor 71g is an evaporator pressure detection unit that detects the refrigerant evaporation pressure Pe in the indoor evaporator 19. In this embodiment, the evaporator pressure sensor 71g specifically detects the refrigerant pressure on the outlet side of the indoor evaporator 19.

[0129] The outdoor unit temperature sensor 71h is an outdoor unit temperature detection unit that detects the temperature of the refrigerant flowing in the outdoor heat exchanger 18, i.e., the outdoor unit refrigerant temperature T1. In this embodiment, the outdoor unit temperature sensor 71h specifically detects the temperature of the refrigerant on the outlet side of the outdoor heat exchanger 18.

[0130] The outdoor unit pressure sensor 71i is an outdoor unit temperature detection unit that detects the pressure of the refrigerant flowing in the outdoor heat exchanger 18, i.e., the outdoor unit refrigerant pressure Pout. In this embodiment, the outdoor unit pressure sensor 71i specifically detects the pressure of the refrigerant on the outlet side of the outdoor heat exchanger 18.

[0131] The battery temperature sensor 71j is a battery temperature detection unit that detects the temperature of the battery 80, i.e., the battery temperature TB. The battery temperature sensor 71j has multiple temperature detection units, detecting the temperature of multiple parts of the battery 80. Therefore, the control device 70 can also detect the temperature difference between different parts of the battery 80. Furthermore, the average value of the detection values ​​from multiple temperature sensors is used as the battery temperature TB.

[0132] The high-temperature side heat medium temperature sensor 71k is a high-temperature side heat medium temperature detection unit that detects the high-temperature side heat medium temperature TWH flowing into the heater core 52. The low-temperature side heat medium temperature sensor 71m is a low-temperature side heat medium temperature detection unit that detects the low-temperature side heat medium temperature TWL flowing into the cooling water passage 80a of the battery 80.

[0133] Furthermore, the input side of the control device 70 is connected to the operation panel 72 located near the instrument panel at the front of the vehicle interior. Operation signals from various operation switches provided on the operation panel 72 are input to the control device 70. Specific operation switches provided on the operation panel 72 include automatic switches, air conditioning switches, fan speed setting switches, temperature setting switches, etc.

[0134] The automatic switch is an operating switch that sets or deactivates the automatic control operation of the refrigeration cycle device 10. The air conditioning switch is an operating switch that requires cooling of the supplied air through the indoor evaporator 19. The airflow setting switch is an operating switch that manually sets the airflow of the indoor fan 42. The temperature setting switch is an operating switch that sets the target temperature Tset inside the vehicle.

[0135] Furthermore, the control device 70 of this embodiment is a component that integrates a control unit for controlling various controllable devices connected to its output side. Therefore, the structure (i.e., hardware and software) for controlling the operation of each controllable device constitutes the control unit for controlling the operation of each controllable device.

[0136] For example, the structure in the control device 70 that controls the operation of the first on / off valve 14a to the fourth on / off valve 14d, which are refrigerant circuit switching units, constitutes the refrigerant circuit control unit 70a.

[0137] Next, the operation of the vehicle air conditioning unit of this embodiment with the above-described configuration will be explained. The refrigeration cycle unit 10 is configured to switch the refrigerant circuit according to various operating modes for air conditioning inside the vehicle and cooling of the battery 80.

[0138] The vehicle air conditioning unit 1 has eight operating modes: (a) cooling mode, (b) independent cooling mode, (c) cooling and cooling mode, (d) outdoor air heating mode, (e) waste heat heating mode, (f) outdoor air waste heat heating mode, (g) outdoor air parallel dehumidification heating mode, and (h) waste heat parallel dehumidification heating mode.

[0139] These operating modes are switched by executing a control program. The control program is executed when the automatic switch on the operation panel 72 is turned on and the automatic control of the refrigeration cycle device 10 is set. In the control program, the detection signals from the aforementioned sensor group and the operation signals from the operation panel 72 are read in at predetermined intervals, and the operating mode is switched appropriately.

[0140] More specifically, the control program switches the operating mode based on the outside air temperature Tam, the target airflow temperature TAO, and the operating signal of the air conditioning switch on the control panel 72. The target airflow temperature TAO is the target temperature of the air blown into the vehicle interior.

[0141] The target blowout temperature TAO is calculated using the following formula F3.

[0142] TAO=Kset×Tset-Kr×Tr-Kam×Tam-Ks×Ts+C…(F3)

[0143] Additionally, Tset is the set interior temperature via a temperature setting switch. Tr is the interior temperature detected by the interior air sensor. Tam is the exterior temperature detected by the exterior air sensor. Ts is the amount of sunlight detected by the sunlight sensor. Kset, Kr, Kam, and Ks are control gains, and C is a constant used for calibration.

[0144] In addition, the control program determines whether to cool the battery 80 based on the battery temperature TB detected by the battery temperature sensor 71j. The detailed operation of each operating mode is explained below.

[0145] (a) Cooling mode

[0146] The cooling mode is an operation mode that cools the vehicle interior by blowing cooled air into the vehicle instead of cooling the battery 80.

[0147] In cooling mode, control device 70 closes the first on / off valve 14a, opens the second on / off valve 14b, closes the third on / off valve 14c, and closes the fourth on / off valve 14d. Additionally, control device 70 sets the heating expansion valve 16a to fully open, the cooling expansion valve 16b to a throttling state to reduce refrigerant pressure, and the cooling expansion valve 16c to fully close.

[0148] Thus, the refrigeration cycle device 10 in refrigeration mode is switched to a refrigerant circuit in which the refrigerant discharged from the compressor 11 circulates sequentially through the water refrigerant heat exchanger 12, the heating expansion valve 16a, the outdoor heat exchanger 18, the refrigeration fixed throttling component 23b, the receiver section 15, the refrigeration expansion valve 16b, the indoor evaporator 19, and the suction port of the compressor 11.

[0149] In the refrigerant circuit of the cooling mode, the refrigerant flowing out from the outdoor heat exchanger 18, which serves as the outdoor heat exchange section, flows into the fixed throttling member 23b, which serves as the pressure reducing section on the receiver side. The refrigerant flowing out from the receiver section 15 flows into the expansion valve 16b, which serves as the pressure reducing section on the evaporator side. The refrigerant, whose pressure has been reduced by the expansion valve 16b, flows into the indoor evaporator 19, which serves as the evaporator section. Therefore, the refrigerant circuit of the cooling mode is included in the first circuit.

[0150] In the above-described loop structure, the control device 70 appropriately controls the operation of various controlled devices. For example, for the compressor 11, the control device 70 controls the discharge capacity so that the evaporator temperature Te detected by the evaporator temperature sensor 71f is close to the target evaporator temperature TEO. The target evaporator temperature TEO is determined based on the target discharge temperature TEO and with reference to a control mapping diagram for refrigeration modes pre-stored in the control device 70.

[0151] In addition, for the expansion valve 16b used for refrigeration, the control device 70 controls the throttling opening so that the superheat SH1 of the refrigerant on the outlet side of the indoor evaporator 19 is close to the target superheat KSH.

[0152] Additionally, for the indoor air supply fan 42, the control device 70 controls the air supply capacity based on the target blow-out temperature TAO and with reference to a control mapping diagram pre-stored in the control device 70. Furthermore, for the air mixing door 44, the control device 70 controls the opening degree of the air mixing door 44 so that the blow-out air temperature TAV detected by the air conditioning air temperature sensor 71e is close to the target blow-out temperature TAO.

[0153] Furthermore, for the high-temperature side heat medium pump 51, the control device 70 operates it to achieve a predetermined pressure delivery capacity. Similarly, for the low-temperature side heat medium pump 61, the control device 70 operates it to achieve a predetermined pressure delivery capacity. Therefore, in the refrigeration cycle device 10 in cooling mode, a vapor compression refrigeration cycle is configured, where the water refrigerant heat exchanger 12 and the outdoor heat exchanger 18 function as condensers, and the indoor evaporator 19 functions as an evaporator.

[0154] In addition, in the high-temperature side heat medium circuit 50 of the cooling mode, the high-temperature side heat medium heated by the water refrigerant heat exchanger 12 is pressurized to the heater core 52.

[0155] In addition, in the cooling mode of the indoor air conditioning unit 40, a portion of the supply air cooled by the indoor evaporator 19 is reheated by the heater core 52, and the temperature-adjusted supply air is blown into the vehicle interior. Thus, cooling of the vehicle interior is achieved.

[0156] (b) Individual Cooling Mode

[0157] The standalone cooling mode is an operating mode that cools the battery 80 without regulating the air inside the vehicle.

[0158] In standalone cooling mode, control device 70 closes the first on / off valve 14a, opens the second on / off valve 14b, closes the third on / off valve 14c, and closes the fourth on / off valve 14d. Additionally, control device 70 sets the heating expansion valve 16a to fully open, the cooling expansion valve 16b to fully closed, and the cooling expansion valve 16c to a throttling state.

[0159] Thus, the refrigeration cycle device 10 in the single cooling mode is switched to a refrigerant circuit in which the refrigerant discharged from the compressor 11 circulates sequentially through the water refrigerant heat exchanger 12, the heating expansion valve 16a, the outdoor heat exchanger 18, the cooling fixed throttling component 23b, the receiver section 15, the cooling expansion valve 16c, the chiller 20, and the suction port of the compressor 11.

[0160] Furthermore, in the refrigerant circuit of the separate cooling mode, the refrigerant flowing out from the outdoor heat exchanger 18, which serves as the outdoor heat exchange section, flows into the fixed throttling member 23b, which serves as the pressure reducing section on the receiver side. The refrigerant flowing out from the receiver section 15 flows into the cooling expansion valve 16c, which serves as the pressure reducing section on the evaporator side. The refrigerant pressure reduced by the cooling expansion valve 16c flows into the chiller 20, which serves as the evaporator. Therefore, the refrigerant circuit of the separate cooling mode is included in the first circuit.

[0161] In the aforementioned circuit structure, the control device 70 appropriately controls the operation of various controlled devices. For example, for the compressor 11, the control device 70 controls the discharge capacity to achieve the discharge capacity required for a predetermined individual cooling mode. Additionally, for the cooling expansion valve 16c, the control device 70 controls the throttling opening to ensure that the superheat SH2 of the refrigerant at the outlet side of the refrigerant passage of the chiller 20 is close to the target superheat KSH.

[0162] Additionally, the control device 70 stops the indoor fan 42. Furthermore, the control device 70 activates the high-temperature side heat medium pump 51 to achieve its pressure delivery capacity. Additionally, the control device 70 activates the low-temperature side heat medium pump 61 to achieve a predetermined pressure delivery capacity. Therefore, in the refrigeration cycle device 10 with a separate cooling mode, a vapor compression refrigeration cycle is configured, in which the outdoor heat exchanger 18 functions as a condenser and the chiller 20 functions as an evaporator.

[0163] Additionally, in the low-temperature side heat transfer medium circuit 60 of the separate cooling mode, the low-temperature side heat transfer medium cooled by the chiller 20 flows into the cooling water passage 80a of the battery 80. As a result, the battery 80 is cooled.

[0164] (c) Cooling mode

[0165] The cooling mode is an operation mode that cools the battery 80 and cools the vehicle interior by blowing cooled air into the vehicle interior.

[0166] In cooling mode, control device 70 closes the first on / off valve 14a, opens the second on / off valve 14b, closes the third on / off valve 14c, and closes the fourth on / off valve 14d. Additionally, control device 70 sets the heating expansion valve 16a to fully open, the cooling expansion valve 16b to throttling mode, and the cooling expansion valve 16c to throttling mode.

[0167] Thus, in the refrigeration cycle device 10 of the cooling mode, the refrigerant discharged from the compressor 11 flows in the following sequence: water refrigerant heat exchanger 12, heating expansion valve 16a, outdoor heat exchanger 18, cooling fixed throttling component 23b, and receiver section 15. Furthermore, the refrigerant flowing from the receiver section 15 is switched to circulate in the following sequence: cooling expansion valve 16b, indoor evaporator 19, and compressor 11 suction inlet; and in the following sequence: cooling expansion valve 16c, chiller 20, and compressor 11 suction inlet.

[0168] That is, in the cooling mode, the refrigerant circuit is switched to a parallel connection between the indoor evaporator 19 and the chiller 20 relative to the refrigerant flow.

[0169] Furthermore, in the refrigerant circuit of the cooling mode, the refrigerant flowing out from the outdoor heat exchanger 18, which serves as the outdoor heat exchange section, flows into the fixed throttling member 23b, which serves as the pressure reducing section on the receiver side. The refrigerant flowing out from the receiver section 15 flows into the expansion valve 16b and the expansion valve 16c, which serve as the pressure reducing section on the evaporator side. The refrigerant pressure-reduced by the expansion valve 16b flows into the indoor evaporator 19, which serves as the evaporator section, and the refrigerant pressure-reduced by the expansion valve 16c flows into the chiller 20, which serves as the evaporator section. Therefore, the refrigerant circuit of the cooling mode is included in the first circuit.

[0170] In the aforementioned loop structure, the control device 70 appropriately controls the operation of various controlled devices. For example, the control device 70 controls the compressor 11 and the refrigeration expansion valve 16b in the same way as in the refrigeration mode. Furthermore, the control device 70 controls the throttling opening of the cooling expansion valve 16c to achieve a predetermined throttling opening for the refrigeration / cooling mode. The control device 70 controls other controlled devices in the same way as in the refrigeration mode.

[0171] Therefore, in the refrigeration cycle device 10 of the refrigeration cooling mode, a vapor compression refrigeration cycle is configured in which the water refrigerant heat exchanger 12 and the outdoor heat exchanger 18 function as condensers, and the indoor evaporator 19 and the chiller 20, which are connected in parallel with each other relative to the refrigerant flow, function as evaporators.

[0172] In addition, in the high-temperature side heat medium circuit 50 of the cooling mode, the high-temperature side heat medium heated by the water refrigerant heat exchanger 12 is pressurized to the heater core 52. Meanwhile, in the low-temperature side heat medium circuit 60 of the cooling mode, the low-temperature side heat medium cooled by the chiller 20 flows into the cooling water passage 80a of the battery 80. Thus, the battery 80 is cooled.

[0173] In addition, in the cooling mode of the indoor air conditioning unit 40, a portion of the supply air cooled by the indoor evaporator 19 is reheated by the heater core 52, and the temperature-adjusted supply air is blown into the vehicle interior. Thus, cooling of the vehicle interior is achieved.

[0174] (d) External air heating mode

[0175] The external air heating mode is an operating mode that heats the vehicle interior by blowing heated air into the vehicle interior instead of cooling the battery 80.

[0176] In the outside gas heating mode, the control device 70 opens the first on-off valve 14a, closes the second on-off valve 14b, opens the third on-off valve 14c, and opens the fourth on-off valve 14d. In addition, the control device 70 sets the heating expansion valve 16a to a throttling state, sets the cooling expansion valve 16b to a fully closed state, and sets the cooling expansion valve 16c to a fully closed state.

[0177] Thus, the refrigeration cycle device 10 in the outdoor heating mode is switched to a refrigerant circuit in which the refrigerant discharged from the compressor 11 circulates sequentially through the water refrigerant heat exchanger 12, the heating fixed throttling component 23a, the receiver 15, the heating expansion valve 16a, the outdoor heat exchanger 18, and the suction port of the compressor 11.

[0178] In the above-described loop structure, the control device 70 appropriately controls the operation of various controlled devices. For example, for the compressor 11, the control device 70 controls the discharge capacity so that the high-temperature side heat medium temperature TWH detected by the high-temperature side heat medium temperature sensor 71k is close to the predetermined target high-temperature side heat medium temperature TWHO.

[0179] Additionally, for the heating expansion valve 16a, the control device 70 controls the throttling opening to bring the superheat SH3 of the refrigerant at the outlet side of the outdoor heat exchanger 18 close to the target superheat KSH. For other controlled equipment, the control device 70 performs the same control as in the cooling mode.

[0180] Therefore, in the refrigeration cycle device 10 of the outside air heating mode, a vapor compression refrigeration cycle is configured in which the water refrigerant heat exchanger 12 functions as a condenser and the outdoor heat exchanger 18 functions as an evaporator.

[0181] In addition, in the high-temperature side heat medium circuit 50 of the external gas heating mode, the high-temperature side heat medium heated by the water refrigerant heat exchanger 12 is pressurized to the heater core 52.

[0182] In addition, in the outdoor air heating mode of the indoor air conditioning unit 40, the supply air heated by the heater core 52 is blown into the vehicle interior. This achieves heating of the vehicle interior. That is, the outdoor air heating mode is an operating mode that uses the heat absorbed by the refrigerant from the outside air through the outdoor heat exchanger 18 as a heat source to heat the supply air.

[0183] (e) Waste heat heating mode

[0184] The waste heat heating mode is an operation mode that cools the battery 80 and heats the vehicle interior by blowing heated air into the vehicle interior.

[0185] In waste heat heating mode, control device 70 opens the first on / off valve 14a, closes the second on / off valve 14b, closes the third on / off valve 14c, and closes the fourth on / off valve 14d. Additionally, control device 70 sets the heating expansion valve 16a to a fully closed state, the cooling expansion valve 16b to a fully closed state, and the cooling expansion valve 16c to a throttling state.

[0186] Thus, the refrigeration cycle device 10 in waste heat heating mode is switched to a refrigerant circuit in which the refrigerant discharged from the compressor 11 circulates sequentially through the water refrigerant heat exchanger 12, the heating fixed throttling component 23a, the receiver section 15, the cooling expansion valve 16c, the chiller 20, and the suction port of the compressor 11.

[0187] Furthermore, in the refrigerant circuit of the waste heat heating mode, the refrigerant flowing out from the water refrigerant heat exchanger 12, which serves as a heat dissipation section, flows into the fixed throttling member 23a for heating, which serves as a pressure reducing section on the receiver side. The refrigerant flowing out from the receiver section 15 flows into the cooling expansion valve 16c, which serves as a pressure reducing section on the evaporator side. The refrigerant, after being pressure-reduced by the cooling expansion valve 16c, flows into the chiller 20, which serves as the evaporator. Therefore, the refrigerant circuit of the waste heat heating mode is included in the second circuit.

[0188] In the aforementioned circuit structure, the control device 70 appropriately controls the operation of various controlled devices. For example, the control device 70 controls the compressor 11 in the same way as in the outside air heating mode. Additionally, for the cooling expansion valve 16c, the control device 70 controls the throttling opening to bring the superheat SH2 of the refrigerant at the outlet of the refrigerant passage of the chiller 20 close to the target superheat KSH. For other controlled devices, the control device 70 controls them in the same way as in the cooling mode.

[0189] Therefore, in the refrigeration cycle device 10 of the waste heat heating mode, a vapor compression refrigeration cycle is configured in which the water refrigerant heat exchanger 12 functions as a condenser and the chiller 20 functions as an evaporator.

[0190] In addition, in the high-temperature side heat medium circuit 50 of the waste heat heating mode, the high-temperature side heat medium heated by the water refrigerant heat exchanger 12 is pressurized to the heater core 52. Meanwhile, in the low-temperature side heat medium circuit 60 of the waste heat heating mode, the low-temperature side heat medium cooled by the chiller 20 flows into the cooling water passage 80a of the battery 80. Thus, the battery 80 is cooled.

[0191] In addition, in the waste heat heating mode of the indoor air conditioning unit 40, the supply air heated by the heater core 52 is blown into the vehicle interior. This achieves heating of the vehicle interior. That is, the waste heat heating mode is an operating mode that uses the waste heat absorbed by the refrigerant from the low-temperature side heat medium of the battery 80 through the chiller 20 as a heat source to heat the supply air.

[0192] (f) External air waste heat heating mode

[0193] The external air waste heat heating mode is an operation mode that cools the battery 80 and heats the vehicle interior by blowing in air that has been heated to a higher heating capacity than the external air heating mode or waste heat heating mode.

[0194] In the external waste heat heating mode, the control device 70 opens the first on / off valve 14a, closes the second on / off valve 14b, opens the third on / off valve 14c, and opens the fourth on / off valve 14d. Additionally, the control device 70 sets the heating expansion valve 16a to a throttling state, the cooling expansion valve 16b to a fully closed state, and the cooling expansion valve 16c to a throttling state.

[0195] Thus, the refrigeration cycle device 10 in the outdoor waste heat heating mode causes the refrigerant discharged from the compressor 11 to flow in the order of water refrigerant heat exchanger 12, heating fixed throttling component 23a, and receiver section 15. Furthermore, the refrigerant flowing from the receiver section 15 is switched to circulate in the order of heating expansion valve 16a, outdoor heat exchanger 18, and compressor 11 suction inlet, and in the order of cooling expansion valve 16c, chiller 20, and compressor 11 suction inlet in a refrigerant circuit.

[0196] That is, in the outdoor waste heat heating mode, the refrigerant circuit is switched to be connected in parallel with the outdoor heat exchanger 18 and the chiller 20 relative to the refrigerant flow.

[0197] Furthermore, in the refrigerant circuit of the outdoor waste heat heating mode, the refrigerant flowing out from the water refrigerant heat exchanger 12, which serves as a heat dissipation section, flows into the fixed throttling member 23a, which serves as a pressure reducing section on the receiver side. The refrigerant flowing out from the receiver section 15 flows into the cooling expansion valve 16c, which serves as a pressure reducing section on the evaporator side. The refrigerant, after being pressure-reduced by the cooling expansion valve 16c, flows into the chiller 20, which serves as the evaporator. Therefore, the refrigerant circuit of the outdoor waste heat heating mode is included in the second circuit.

[0198] In the aforementioned circuit structure, the control device 70 appropriately controls the operation of various controlled devices. For example, the control device 70 controls the compressor 11 and the heating expansion valve 16a in the same way as in the outside air heating mode. Furthermore, the control device 70 controls the throttling opening of the cooling expansion valve 16c to a predetermined throttling opening for the outside air waste heat heating mode. For other controlled devices, the control device 70 controls them in the same way as in the cooling mode.

[0199] Therefore, in the refrigeration cycle device 10 of the external air waste heat heating mode, a vapor compression refrigeration cycle is configured in which the water refrigerant heat exchanger 12 functions as a condenser, and the outdoor heat exchanger 18 and the chiller 20, which are connected in parallel with each other relative to the refrigerant flow, function as evaporators.

[0200] In addition, in the high-temperature side heat medium circuit 50 of the external gas waste heat heating mode, the high-temperature side heat medium heated by the water refrigerant heat exchanger 12 is pressurized to the heater core 52. Meanwhile, in the low-temperature side heat medium circuit 60 of the external gas waste heat heating mode, the low-temperature side heat medium cooled by the chiller 20 flows into the cooling water passage 80a of the battery 80. Thus, the battery 80 is cooled.

[0201] In addition, in the indoor air conditioning unit 40 using the external air waste heat heating mode, the supplied air heated by the heater core 52 is blown into the vehicle interior. This achieves heating of the vehicle interior.

[0202] In other words, the outdoor waste heat heating mode is an operating mode that uses the heat absorbed by the refrigerant from the outdoor air through the outdoor heat exchanger 18 and the waste heat absorbed by the refrigerant from the low-temperature side heat medium of the battery 80 through the chiller 20 as heat sources to heat the supply air. Therefore, it can heat the supply air with a higher heating capacity than the waste heat heating mode.

[0203] (g) External air parallel dehumidification and heating mode

[0204] The external air parallel dehumidification and heating mode does not cool the battery 80, but instead reheats the cooled and dehumidified air supply and blows it into the vehicle interior to dehumidify and heat the vehicle interior.

[0205] In the parallel dehumidification and heating mode of the outside air, the control device 70 opens the first on-off valve 14a, closes the second on-off valve 14b, opens the third on-off valve 14c, and opens the fourth on-off valve 14d. Additionally, the control device 70 sets the heating expansion valve 16a to a throttling state, the cooling expansion valve 16b to a throttling state, and the cooling expansion valve 16c to a fully closed state.

[0206] Thus, the refrigeration cycle device 10 in the parallel dehumidification and heating mode of the outside air causes the refrigerant discharged from the compressor 11 to flow in the order of water refrigerant heat exchanger 12, heating fixed throttling component 23a, and receiver section 15. Moreover, the refrigerant flowing out of the receiver section 15 is switched to circulate in the order of heating expansion valve 16a, outdoor heat exchanger 18, and compressor 11 suction inlet, and in the order of cooling expansion valve 16b, indoor evaporator 19, and compressor 11 suction inlet inlet.

[0207] That is, in the parallel dehumidification and heating mode of the outside air, the refrigerant circuit is switched to be connected in parallel with the refrigerant flow between the outdoor heat exchanger 18 and the indoor evaporator 19.

[0208] Furthermore, in the refrigerant circuit of the parallel dehumidification and heating mode for outside air, the refrigerant flowing out from the water refrigerant heat exchanger 12, which serves as a heat dissipation section, flows into the fixed throttling member 23a for heating, which serves as a pressure reducing section on the receiver side. The refrigerant flowing out from the receiver section 15 flows into the expansion valve 16b for refrigeration, which serves as a pressure reducing section on the evaporator side. The refrigerant pressure reduced by the expansion valve 16b flows into the indoor evaporator 19, which serves as the evaporator section. Therefore, the refrigerant circuit of the parallel dehumidification and heating mode for outside air is included in the second circuit.

[0209] In the aforementioned circuit structure, the control device 70 appropriately controls the operation of various controlled devices. For example, the control device 70 controls the compressor 11 and the heating expansion valve 16a in the same way as in the outside air heating mode. Furthermore, the control device 70 controls the throttling opening of the cooling expansion valve 16b to achieve a predetermined throttling opening for the outside air parallel dehumidification heating mode. For other controlled devices, the control device 70 controls them in the same way as in the cooling mode.

[0210] Therefore, in the refrigeration cycle device 10 of the parallel dehumidification and heating mode of the outside air, a vapor compression refrigeration cycle is configured in which the water refrigerant heat exchanger 12 functions as a condenser and the outdoor heat exchanger 18 and the indoor evaporator 19, which are connected in parallel with each other relative to the refrigerant flow, function as evaporators.

[0211] In addition, in the high-temperature side heat medium circuit 50 of the external air parallel dehumidification and heating mode, the high-temperature side heat medium heated by the water refrigerant heat exchanger 12 is pressurized to the heater core 52.

[0212] In addition, in the indoor air conditioning unit 40 in the parallel dehumidification and heating mode of the outside air, the supply air cooled and dehumidified by the indoor evaporator 19 is reheated by the heater core 52 and blown into the vehicle interior. Thus, dehumidification and heating are achieved in the vehicle interior.

[0213] (h) Waste heat parallel dehumidification and heating mode

[0214] The waste heat parallel dehumidification and heating mode is an operation mode that cools the battery 80 and blows the cooled and dehumidified air into the vehicle interior to dehumidify and heat the vehicle interior.

[0215] In the waste heat parallel dehumidification heating mode, the control device 70 opens the first on-off valve 14a, closes the second on-off valve 14b, opens the third on-off valve 14c, and opens the fourth on-off valve 14d. Additionally, the control device 70 sets the heating expansion valve 16a to a throttling state, the cooling expansion valve 16b to a throttling state, and the cooling expansion valve 16c to a throttling state.

[0216] Thus, the refrigeration cycle device 10 in the waste heat parallel dehumidification and heating mode causes the refrigerant discharged from the compressor 11 to flow in the order of water refrigerant heat exchanger 12, heating fixed throttling component 23a, and receiver section 15. Moreover, the refrigerant flowing out of the receiver section 15 is switched to circulate in the order of heating expansion valve 16a, outdoor heat exchanger 18, and compressor 11 suction port, and also in the order of cooling expansion valve 16b, indoor evaporator 19, and compressor 11 suction port, and also in the order of cooling expansion valve 16c, chiller 20, and compressor 11 suction port.

[0217] That is, in the waste heat parallel dehumidification heating mode, the refrigerant circuit is switched to a parallel connection between the outdoor heat exchanger 18, the indoor evaporator 19, and the chiller 20 and the refrigerant flow.

[0218] Furthermore, in the refrigerant circuit of the waste heat parallel dehumidification heating mode, the refrigerant flowing out from the water refrigerant heat exchanger 12, which serves as a heat dissipation section, flows into the fixed throttling member 23a for heating, which serves as a pressure reducing section on the receiver side. The refrigerant flowing out from the receiver section 15 flows into the refrigeration expansion valve 16b and the cooling expansion valve 16c, which serve as pressure reducing sections on the evaporator side. The refrigerant pressure-reduced by the refrigeration expansion valve 16b flows into the indoor evaporator 19, which serves as an evaporator section, and the refrigerant pressure-reduced by the cooling expansion valve 16c flows into the chiller 20, which serves as an evaporator section. Therefore, the refrigerant circuit of the waste heat parallel dehumidification heating mode is included in the second circuit.

[0219] In the aforementioned circuit structure, the control device 70 appropriately controls the operation of various controlled devices. For example, the control device 70 controls the compressor 11 and the heating expansion valve 16a in the same way as in the outside air heating mode. Furthermore, the control device 70 controls the throttling opening of the cooling expansion valve 16b and the cooling expansion valve 16c to achieve a predetermined throttling opening for the waste heat parallel dehumidification heating mode. For other controlled devices, the control device 70 controls them in the same way as in the cooling mode.

[0220] Therefore, in the refrigeration cycle device 10 of the waste heat parallel dehumidification and heating mode, a vapor compression refrigeration cycle is configured in which the water refrigerant heat exchanger 12 functions as a condenser and the outdoor heat exchanger 18, indoor evaporator 19 and chiller 20, which are connected in parallel with each other relative to the refrigerant flow, function as evaporators.

[0221] In addition, in the high-temperature side heat medium circuit 50 of the waste heat parallel dehumidification heating mode, the high-temperature side heat medium heated by the water refrigerant heat exchanger 12 is pressurized to the heater core 52. Meanwhile, in the low-temperature side heat medium circuit 60 of the waste heat parallel dehumidification heating mode, the low-temperature side heat medium cooled by the chiller 20 flows into the cooling water passage 80a of the battery 80. Thus, the battery 80 is cooled.

[0222] In addition, in the indoor air conditioning unit 40 with waste heat parallel dehumidification and heating mode, the supply air cooled and dehumidified by the indoor evaporator 19 is reheated by the heater core 52 and blown into the vehicle interior. Thus, dehumidification and heating are achieved in the vehicle interior.

[0223] As described above, the refrigeration cycle device 10 can operate in various modes by switching the refrigerant circuit. Therefore, in the vehicle air conditioning system, it is possible to appropriately adjust the temperature of the battery 80 while simultaneously achieving comfortable air conditioning inside the vehicle.

[0224] Furthermore, in the refrigeration cycle apparatus 10 of this embodiment, under any operating mode, the high-pressure liquid refrigerant flowing out from the heat exchange section, which functions as a condenser, flows into the fixed throttling member 23a for heating or the fixed throttling member 23b for cooling, which functions as a pressure reducing section on the receiver side. Therefore, compared with the refrigerant on the outlet side of the heat exchange section, which functions as a condenser, the saturation pressure of the refrigerant in the receiver section 15 can be reduced.

[0225] Therefore, the enthalpy of the refrigerant in the receiver section 15 can be lower than the enthalpy of the refrigerant at the outlet side of the heat exchange section, which functions as a condenser, due to the slope of the saturated liquid line on the Morrillon diagram. Thus, the refrigerant at the outlet side of the heat exchange section, which functions as a condenser, can be subcooled. Furthermore, the enthalpy of the refrigerant flowing from the receiver section 15 into the heat exchange section, which functions as an evaporator, can be reduced.

[0226] In addition, in the refrigeration cycle device 10, under any operating mode, the refrigerant gas-liquid separation is performed on the receiver-side pressure reducing section, and the separated liquid refrigerant is stored in the receiver section 15 as residual refrigerant for the cycle. Therefore, the refrigerant at the outlet side of the heat exchange section, which functions as an evaporator, can be made to have superheat. Then, the enthalpy of the refrigerant at the outlet side of the heat exchange section, which functions as an evaporator, can increase.

[0227] As a result, the refrigeration cycle apparatus 10 according to this embodiment can increase the enthalpy difference obtained by subtracting the enthalpy of the inlet-side refrigerant from the enthalpy of the outlet-side refrigerant in the heat exchange section that functions as an evaporator, regardless of the operating mode. That is, it can increase the amount of heat absorbed by the refrigerant in the heat exchange section that functions as an evaporator, thereby improving the COP of the refrigeration cycle apparatus 10.

[0228] However, in a refrigeration cycle apparatus like the refrigeration cycle apparatus 10 of this embodiment, where the refrigerant circuit is switched according to the operating mode, the necessary circulating refrigerant flow rate that circulates in the cycle can easily change depending on the operating mode. For example, compared to other operating modes, the circulating refrigerant flow rate is more likely to increase in operating modes with higher heat loads or larger internal volumes of the cycle.

[0229] According to the inventors' research, in the refrigeration cycle device 10, the refrigerant circulation flow rate is greater in the first circuit operation mode compared to the second circuit operation mode.

[0230] Specifically, in the refrigeration cycle unit 10, under conditions such as (g) parallel dehumidification and heating mode for outside air and (h) parallel dehumidification and heating mode for waste heat, where the temperature difference between outside air and supply air is relatively small, the heat load is easily reduced. Moreover, in the (e) waste heat heating mode where the supply air is heated with a relatively low heating capacity, the internal volume of the cycle also decreases. Therefore, it can be seen that the refrigerant flow rate is the lowest compared to other operating modes.

[0231] Furthermore, in cooling mode (a) and cooling-cooling mode (c), where the temperature difference between the outside air and the supply air is relatively large, the heat load tends to be higher. Moreover, in cooling-cooling mode (c), the internal volume of the refrigerant circulation also increases, thus indicating that the refrigerant flow rate is the highest compared to other operating modes.

[0232] Therefore, in (e) waste heat heating mode, the amount of residual refrigerant stored in receiver section 15 is the largest. Conversely, in (c) cooling mode, the amount of residual refrigerant stored in receiver section 15 is the smallest. Therefore, in the refrigeration cycle device 10, in order to ensure that receiver section 15 can perform sufficient gas-liquid separation performance in (c) cooling mode, the amount of refrigerant introduced needs to be determined.

[0233] The reason is that if the amount of remaining refrigerant stored in the receiver section 15 decreases, the possibility that the separated gaseous refrigerant will re-mix with the liquid refrigerant to become a gas-liquid mixture and flow out of the receiver section 15 increases. Furthermore, if the gas-liquid mixture flows out of the receiver section 15, the enthalpy of the refrigerant flowing into the heat exchange section, which functions as an evaporator, increases, and therefore, the aforementioned COP improvement effect cannot be obtained.

[0234] In response to this, the refrigeration cycle apparatus 10 of this embodiment includes a collision plate 33 as a deceleration unit. Therefore, even when switching to an operating mode where the circulating refrigerant flow rate increases and the amount of remaining refrigerant stored in the receiver section 15 decreases, the reduction in the gas-liquid separation performance of the receiver section 15 can be suppressed.

[0235] In the refrigeration cycle device 10, when the refrigerant is depressurized by the heating fixed throttling member 23a or the cooling fixed throttling member 23b, which serves as a pressure reducing section on the receiver side, the refrigerant flow rate increases. Therefore, in the refrigeration cycle device 10, by using a deceleration section to reduce the flow rate of the refrigerant flowing into the receiver section 15, it is effective in suppressing the deterioration of the gas-liquid separation performance of the receiver section 15.

[0236] Therefore, in the refrigeration cycle device 10, in the (c) refrigeration cooling mode, the increase in the amount of refrigerant required for the receiver unit 15 to achieve sufficient gas-liquid separation performance can be minimized. As a result, even if the refrigeration cycle device 10 is configured to switch refrigerant circuits, the enlargement of the receiver unit 15 can be suppressed. Moreover, the overall configurability and manufacturability of the refrigeration cycle device 10 can be prevented from deteriorating.

[0237] Furthermore, in the refrigeration cycle apparatus 10 of this embodiment, a collision plate 33 having a collision section 33a and a connecting section 33b is used as a deceleration section. Therefore, by causing the refrigerant flowing into the receiver section 15 to collide with the collision section 33a, the flow rate of the refrigerant can be reliably reduced. Furthermore, the heavier liquid refrigerant in the reduced flow rate can fall downwards through the through hole 33c of the connecting section 33b into the lower side of the internal space 15a of the receiver section 15.

[0238] Furthermore, in this embodiment, the number N of through holes 33c and the total opening area SA are determined such that the dimensionless parameter P1 defined by formula F1 satisfies formula F2. Therefore, in practical application, within the range where through holes 33c can be formed in the collision plate 33, foaming of the liquid refrigerant accumulated in the internal space 15a of the receiver section 15 can be suppressed. Thus, the reduction in the COP of the refrigeration cycle device 10 can be suppressed.

[0239] Furthermore, since the collision plate 33 is disposed above the center of the internal space 15a of the receiver section 15, even if the refrigerant collides with the collision plate 33a, it is difficult to affect the liquid level of the liquid refrigerant stored in the internal space 15a of the receiver section 15. Therefore, although the collision plate 33 according to this embodiment has a simple structure, it can improve the gas-liquid separation performance of the receiver section 15.

[0240] Furthermore, in this embodiment, the receiver assembly 30 is disclosed to integrate at least the receiver-side pressure reducing section, the deceleration section, and the receiver section 15. In other words, in this embodiment, the receiver assembly 30, which includes the receiver-side pressure reducing section and the receiver section, is disclosed to include a deceleration section in order to improve gas-liquid separation performance without increasing the size of the receiver section.

[0241] This reduces the space required for configuring each component of the refrigeration cycle device 10, thereby improving the productivity and miniaturizing the refrigeration cycle device 10.

[0242] In addition, the receiver assembly 30 in this embodiment includes a switching block 31 and a depressurization block 32.

[0243] Therefore, by installing the first on / off valve 14a to the third on / off valve 14c, the heating expansion valve 16a, the second check valve 17b, etc., onto the switching block 31, the receiver assembly 30 can be easily formed. Furthermore, by installing the first check valve 17a, the heating fixed throttling component 23a, the cooling fixed throttling component 23b, etc., onto the pressure reducing block 32, the receiver assembly 30 can be easily formed.

[0244] Furthermore, in the receiver assembly 30 of this embodiment, the switching block 31, the pressure reducing block 32, and the receiver section 15 are formed from different components. Moreover, the switching block 31, the pressure reducing block 32, and the receiver section 15 are integrated in such a way that the switching block 31 is in contact with the pressure reducing block 32, the pressure reducing block 32 is in contact with the receiver section 15, and the switching block 31 is not in contact with the receiver section 15.

[0245] Here, in (a) cooling mode, the high-temperature, high-pressure refrigerant discharged from the compressor 11 flows into the first inlet 31a of the switching block 31. Therefore, the temperature of the switching block 31 may rise to the same extent as that of the high-temperature, high-pressure refrigerant. On the other hand, the refrigerant flowing into the receiver section 15 is depressurized by the heating fixed throttling member 23a or the cooling fixed throttling member 23b, which serves as the receiver-side depressurization unit, regardless of the operating mode. Therefore, its temperature is lower than that of the high-temperature, high-pressure refrigerant.

[0246] To address this, the receiver assembly 30 is integrated in such a way that the switching block 31 does not contact the receiver section 15. This prevents the refrigerant in the receiver section 15 from being heated by the switching block 31, thus preventing so-called heat damage.

[0247] In addition, in the receiver assembly 30 of this embodiment, an example of using a collision plate 33 formed by a plate-shaped member that is configured to extend in the horizontal direction as a deceleration unit has been described, but the deceleration unit is not limited to this.

[0248] For example, such as Figure 8 As shown, the collision plate 33 can also be tilted relative to the horizontal direction. Furthermore, the portion of the collision plate 33 furthest from the inlet pipe 15b can be positioned below the liquid level of the liquid refrigerant in the operating mode where the remaining refrigerant stored in the receiver section is minimized. This allows the heavier liquid refrigerant, whose flow rate decreases upon colliding with the collision section 33a, to move along the collision plate 33 towards the lower side of the internal space 15a. Therefore, the gas-liquid separation performance of the receiver section 15 can be improved.

[0249] In addition, such as Figure 9 As shown, a collision plate 33 can also be formed on a curved surface. Furthermore, with... Figure 8 Similarly, the portion of the collision plate 33 furthest from the inlet pipe 15b can be positioned below the liquid level of the refrigerant when the remaining refrigerant stored in the receiver is at its minimum operating mode. Thus, with Figure 8 Similarly, the liquid refrigerant can be moved along the collision plate 33 towards the lower side of the internal space 15a. Therefore, the gas-liquid separation performance of the receiver section 15 can be improved.

[0250] Alternatively, it can be done through Figure 8 , Figure 9 The collision plate 33 described herein has a connecting portion 33b. When the connecting portion 33b is provided, a through hole 33c can be provided at a location where it will not collide with the refrigerant flowing out from the inlet pipe 15b.

[0251] (Second Implementation)

[0252] In this embodiment, an example of modifying the structure of the deceleration section of the receiver assembly 30 compared to the first embodiment will be described. For example... Figure 10 As shown, the deceleration section of this embodiment is formed by a deceleration refrigerant passage 34, which reverses the flow direction of the refrigerant that flows into the internal space 15a of the receiver section 15 after being depressurized by the heating fixed throttling member 23a or the cooling fixed throttling member 23b, which serves as a receiver-side depressurization section.

[0253] More specifically, in this embodiment, the refrigerant passage 34 for deceleration is formed by an inlet pipe 15b disposed within the internal space 15a of the receiver section 15. In this embodiment, the inlet pipe 15b is bent in such a way that the flow direction of the refrigerant flowing into the internal space 15a of the receiver section 15 is redirected towards the direction of collision with the side of the receiver section 15. Furthermore, in this embodiment, the inlet pipe 15b is bent in such a way that the refrigerant flowing into the internal space 15a collides with the upper side of the vertically oriented central portion of the side of the receiver section 15.

[0254] Therefore, the refrigerant flowing into the internal space 15a of the receiver section 15 collides with the side wall of the receiver section 15, causing its flow velocity to decrease. Furthermore, the heavier liquid refrigerant in the reduced flow velocity falls downwards into the internal space 15a of the receiver section 15. Therefore, the gas-liquid separation performance of the receiver section 15 can be improved by using the deceleration refrigerant passage 34.

[0255] The structure and operation of the other cooling cycle device 10 and receiver assembly 30 are the same as in the first embodiment.

[0256] Therefore, the same effects as in the first embodiment can be obtained in the refrigeration cycle apparatus 10 and receiver assembly 30 of this embodiment. That is, even if the refrigeration cycle apparatus 10 is configured to switch the refrigerant circuit, the enlargement of the receiver section 15 can be suppressed. Furthermore, it is possible to provide a receiver assembly 30 that improves gas-liquid separation performance without causing the receiver section 15 to become larger.

[0257] (Third Implementation)

[0258] like Figure 11 As shown, in this embodiment, an example is described where the structure of the refrigerant passage 34, which serves as a deceleration unit, is modified from that in the second embodiment. In this embodiment, the refrigerant passage 34 for deceleration is directly formed in the pressure reducing block 32.

[0259] The structure and operation of the other cooling cycle device 10 and receiver assembly 30 are the same as in the first embodiment. Therefore, the same effects as in the second embodiment can be obtained in the cooling cycle device 10 and receiver assembly 30 of this embodiment.

[0260] (Fourth Implementation)

[0261] like Figure 12 As shown, in this embodiment, an example is described where the shape of the refrigerant passage 34, which serves as a deceleration section, is modified from that of the third embodiment. The refrigerant passage 34 in this embodiment has multiple pressure-reducing side passages 34a and receiver side passages 34b formed in the pressure-reducing block 32. Furthermore, Figure 12 This is a schematic enlarged cross-sectional view of the vicinity of block 32 in the pressure-reducing section. Additionally, in Figure 12 For clarity of illustration, the diagram of outlet pipe 15c is omitted.

[0262] Multiple pressure-reducing side passages 34a are respectively connected to the outlet side of the receiver-side pressure-reducing section. The receiver assembly 30 of this embodiment includes two receiver-side pressure-reducing sections: a heating fixed throttling member 23a and a cooling fixed throttling member 23b. Therefore, in this embodiment, two pressure-reducing side passages 34a are also provided.

[0263] The two pressure-reducing side passages 34a are arranged on the same plane (a horizontal plane in this embodiment). The two pressure-reducing side passages 34a are arranged to be equidistant from the central axis direction of the receiver section 15 (180° interval in this embodiment). Both pressure-reducing side passages 34a extend from the outer periphery of the receiver section 15 toward the central axis side.

[0264] The receiver-side passage 34b is connected to the downstream portion of the plurality of pressure-reducing side passages 34a. The receiver-side passage 34b is disposed near the central axis of the receiver section 15. The receiver-side passage 34b extends from the upper side to the lower side in the direction of the central axis of the receiver section 15.

[0265] In the refrigerant passage 34 for deceleration in this embodiment, the flow of refrigerant flowing horizontally from the pressure-reducing section on the receiver side is redirected to the vertical direction, thereby reducing the refrigerant flow rate. For example, the gas-liquid two-phase refrigerant flowing from the heating fixed throttling member 23a collides with the gas-liquid two-phase refrigerant present in the pressure-reducing section-side passage 34a on the cooling fixed throttling member 23b side, thus slowing down the flow rate. As a result, the flow rate of refrigerant flowing into the receiver section 15 via the receiver section-side passage 34b can be reduced.

[0266] The structure and operation of the other cooling cycle device 10 and receiver assembly 30 are the same as in the first embodiment.

[0267] Therefore, the same effects as in the first embodiment can be obtained in the refrigeration cycle apparatus 10 and receiver assembly 30 of this embodiment. That is, even if the refrigeration cycle apparatus 10 is configured to switch the refrigerant circuit, the enlargement of the receiver section 15 can be suppressed. Furthermore, it is possible to provide a receiver assembly 30 that improves gas-liquid separation performance without causing the receiver section 15 to become larger.

[0268] (Fifth Implementation)

[0269] like Figure 13 As shown, in this embodiment, an example is described where a secondary container 35 is added to the refrigeration cycle apparatus 10 of the first embodiment. The secondary container 35 is a container that stores a portion of the liquid refrigerant flowing out from the water refrigerant heat exchanger 12, which serves as a heat dissipation unit. The secondary container 35 is disposed in the refrigerant flow path from the outlet of the refrigerant passage of the water refrigerant heat exchanger 12 to the first inlet 31a of the receiver assembly 30.

[0270] The structure and operation of the other cooling cycle device 10 and receiver assembly 30 are the same as in the first embodiment.

[0271] Therefore, the same effects as in the first embodiment can be obtained in the refrigeration cycle apparatus 10 and receiver assembly 30 of this embodiment. That is, even if the refrigeration cycle apparatus 10 is configured to switch the refrigerant circuit, the enlargement of the receiver section 15 can be suppressed. Furthermore, it is possible to provide a receiver assembly 30 that improves gas-liquid separation performance without causing the receiver section 15 to become larger.

[0272] Furthermore, the refrigeration cycle apparatus 10 according to this embodiment, having a secondary storage unit 35, allows for the storage of a portion of the remaining refrigerant in the secondary storage unit 35 during operation modes where the remaining refrigerant charge in the cycle is high. Therefore, it is possible to further suppress the enlargement of the receiver unit 15.

[0273] To explain this in more detail, as described in the first embodiment, in the refrigeration cycle device 10, the refrigerant circulation flow rate when switching to the first loop operating mode is greater than the refrigerant circulation flow rate when switching to the second loop operating mode. That is, the remaining refrigerant charge when switching to the second loop operating mode is greater than the remaining refrigerant charge when switching to the first loop operating mode.

[0274] Additionally, in the first loop operation mode, refrigerant that dissipates heat to the outside air through the outdoor heat exchanger 18 flows into the second inlet 32a of the receiver assembly 30. On the other hand, in the second loop operation mode of the refrigeration cycle device 10, refrigerant that dissipates heat to the high-temperature side heat medium through the water refrigerant heat exchanger 12 flows into the first inlet 31a of the receiver assembly 30.

[0275] Furthermore, in the first loop operation mode, the amount of heating of the supply air is less compared to the second loop operation mode, and therefore, the amount of heat dissipated by the refrigerant in the water refrigerant heat exchanger 12 is also less. Consequently, the dryness of the refrigerant flowing out of the water refrigerant heat exchanger 12 is lower when switching to the second loop operation mode than when switching to the first loop operation mode.

[0276] In other words, the refrigerant flowing into the auxiliary tank 35 when the refrigerant circuit switching unit switches to the second circuit has a lower dryness than the refrigerant flowing into the auxiliary tank 35 when switching to the first circuit. Therefore, in the second circuit operation mode, liquid refrigerant is more likely to flow into the auxiliary tank 35 compared to the first circuit operation mode. As a result, even in operation modes where the amount of residual refrigerant circulating increases, residual refrigerant can still be stored.

[0277] (Sixth Implementation Method)

[0278] like Figure 14As shown, in this embodiment, compared to the fifth embodiment, the auxiliary housing 35 and the receiver assembly 30 are integrated. More specifically, in this embodiment, the auxiliary housing 35 is formed in the refrigerant flow path from the first inlet 31a of the switching block 31 to the first internal tee connector 13a. This allows for the provision of a receiver assembly 30 that further suppresses the enlargement of the receiver section 15.

[0279] The present invention is not limited to the embodiments described above, and various modifications can be made without departing from the spirit of the present invention as follows.

[0280] In the above embodiments, an example of applying the refrigeration cycle device 10 of the present invention to a vehicle air conditioning system installed in an electric vehicle has been described, but the application of the refrigeration cycle device 10 is not limited thereto. For example, it can also be applied to a vehicle air conditioning system installed in a so-called hybrid vehicle that obtains driving force for vehicle travel from both an internal combustion engine and an electric motor.

[0281] Furthermore, while the above-described embodiment illustrates an example of cooling the battery 80, which is the object of temperature regulation, it is not a limitation. For example, vehicle-mounted devices that generate heat during operation, such as electric generators, inverters, PCUs, drive shafts, and control devices for ADAS, may also be used as objects of temperature regulation.

[0282] An electric generator functions as both a motor providing driving force and a generator. An inverter supplies power to the electric generator, etc. A PCU (Power Control Unit) is a power control unit that performs power conversion and distribution. A driveshaft is a power transmission mechanism that integrates a gearbox, differential gears, etc. ADAS (Advanced Driver Assistance Systems) control devices are control devices used in advanced driver assistance systems.

[0283] Furthermore, the application of the refrigeration cycle device 10 is not limited to vehicles. For example, in the above embodiment, it can also be applied to a fixed-position air conditioning unit for air conditioning a computer server room. In this case, the computer server can be the object being cooled.

[0284] The structure of the refrigeration cycle device 10 is not limited to the contents disclosed in the above embodiments.

[0285] In the above embodiments, an example is described in which a heating section for heating the supply air is constructed using the water refrigerant heat exchanger 12 and the various components of the high-temperature side heat medium circuit 50, but the heating section is not limited to this.

[0286] For example, the water refrigerant heat exchanger 12 and the high-temperature side heat medium circuit 50 can be eliminated, and the indoor condenser can be used as the heating element. The indoor condenser is a heat dissipation element that allows the high-pressure refrigerant discharged from the compressor 11 to exchange heat with the supply air after passing through the indoor evaporator 19, thereby dissipating the heat of the high-pressure refrigerant to the supply air. The indoor condenser and the heater core 52 can be arranged in the housing 41 of the indoor air conditioning unit 40 in the same way.

[0287] Furthermore, while the above-described embodiment illustrates an example using a fixed throttling component as the receiver-side pressure reducing unit, a variable throttling mechanism can also be used. In this case, a variable throttling mechanism with the same structure as the heating expansion valve 16a can be used as the receiver-side pressure reducing unit.

[0288] Furthermore, in the above embodiment, an example was described where the cooling unit for cooling the battery 80 is constructed using the chiller 20 and the various components of the low-temperature side heat transfer medium circuit 60; however, the cooling unit is not limited to this. For example, the chiller 20 and the low-temperature side heat transfer medium circuit 60 could be omitted, and the cooling water passage 80a of the battery 80 could be used as the cooling unit, allowing the low-pressure refrigerant, depressurized by the cooling expansion valve 16c, to flow directly. In this case, the cooling water passage 80a is an evaporation unit.

[0289] Furthermore, in the above embodiment, an example was described where the fourth check valve 17d was positioned on the refrigerant outlet side of the indoor evaporator 19. However, an evaporating pressure regulating valve can also be used instead of the fourth check valve 17d. The evaporating pressure regulating valve is a variable throttling component consisting of a mechanical structure that increases the valve opening as the refrigerant pressure on the refrigerant outlet side of the indoor evaporator 19 increases. By using the evaporating pressure regulating valve, the refrigerant evaporation pressure in the indoor evaporator 19 can be maintained above a predetermined reference value.

[0290] Furthermore, while the above-described embodiment illustrates an example using R1234yf as the refrigerant in the refrigeration cycle device 10, it is not a limitation. For example, R134a, R600a, R410A, R404A, R32, R407C, etc., may also be used. Alternatively, a mixed refrigerant, such as a mixture of multiple refrigerants, may also be used.

[0291] Furthermore, in the above embodiment, a cooling cycle device 10 capable of switching to multiple operating modes was described, but the switching of operating modes is not limited. As long as it is configured to be able to switch at least to any one of the operating modes of switching to the first circuit and any one of the operating modes of switching to the second circuit, the miniaturization effect of the receiver unit 15 described above can be obtained.

[0292] Furthermore, the refrigeration cycle device 10 can also be configured to perform other operating modes. For example, it can also be configured to perform a standalone dehumidification and heating mode. In the standalone dehumidification and heating mode, the battery 80 is not cooled, but the cooled and dehumidified air is reheated with a lower heating capacity than the parallel dehumidification and heating mode of the outside air and blown into the vehicle interior to perform dehumidification and heating of the vehicle interior.

[0293] In standalone dehumidification and heating mode, control device 70 opens the first on / off valve 14a, closes the second on / off valve 14b, closes the third on / off valve 14c, and closes the fourth on / off valve 14d. Additionally, control device 70 sets the heating expansion valve 16a to a fully closed state, the cooling expansion valve 16b to a throttling state, and the cooling expansion valve 16c to a fully closed state.

[0294] Therefore, the refrigeration cycle device 10 in the standalone dehumidification and heating mode is switched to a refrigerant circuit in which the refrigerant discharged from the compressor 11 circulates sequentially through the water-refrigerant heat exchanger 12, the heating fixed throttling component 23a, the receiver section 15, the cooling expansion valve 16b, the indoor evaporator 19, and the suction inlet of the compressor 11. The refrigerant circuit in the standalone dehumidification and heating mode is included in the second circuit.

[0295] The structure of the receiver assembly 30 is not limited to that disclosed in the above embodiments. As long as the receiver assembly 30 integrates at least the receiver-side pressure reducing section, the receiver section 15, and the deceleration section, the gas-liquid separation performance can be improved without increasing the size of the receiver section.

[0296] Therefore, if heat damage is to be prioritized, the switching unit block 31 may not need to be integrated. That is, the first on / off valve 14a to the third on / off valve 14c and the heating expansion valve 16a may not need to be integrated into the receiver assembly 30.

[0297] Furthermore, in the first embodiment described above, a collision plate 33 formed of a metal plate-shaped component is used as a deceleration unit, but the deceleration unit is not limited to this. For example, a deceleration unit formed of a filter or desiccant can also be used.

[0298] Furthermore, in the first embodiment described above, an example was given where the through holes 33c of the collision plate 33 were arranged in a ring around the central axis of the receiver portion 15, but this is not a limitation. For example, they could also be arranged in a multi-layered ring shape. Moreover, as long as the regions in the collision plate 33 where the connecting portions 33b are formed are spaced apart by a predetermined interval, they could also be arranged to be spaced apart from each other.

[0299] In addition, in the above embodiments, the refrigerant flows into the internal space 15a from the upper side of the receiver section 15, and the separated liquid refrigerant flows out from the upper side of the receiver section 15, but it is not limited to this.

[0300] For example, such as Figure 15 As shown, the refrigerant can also flow into the internal space 15a from the lower side of the receiver section 15. In this case, the receiver section 15 can be positioned above the pressure reducing block 32. Furthermore, a deceleration refrigerant passage 34 can be formed through the inlet pipe 15b to redirect the flow direction of the refrigerant flowing into the internal space 15a of the receiver section 15 towards the direction of collision with the side of the receiver section 15. Alternatively, the outlet pipe 15c can be omitted, and a refrigerant passage for liquid refrigerant to flow out can be formed in the pressure reducing block 32.

[0301] Furthermore, such as Figure 16 As shown, the refrigerant flowing into the internal space 15a from the lower side of the receiver section 15 can also collide with the top 15d of the receiver section 15. In this case, the top 15d of the receiver section 15 becomes a deceleration section.

[0302] In addition, such as Figure 17 As shown, refrigerant flowing into the internal space 15a from the side of the receiver section 15 can also collide with the side of the receiver section 15. In this case, the side of the receiver section 15 becomes a deceleration part. Furthermore, in Figure 17 In this process, the separated liquid refrigerant flows out from the upper side of the receiver section 15, but it can also be separated from the liquid refrigerant through... Figure 15 , Figure 16 The receiver assembly 30 described also flows out from the lower side.

[0303] The structures of the high-temperature side heat medium circuit 50 and the low-temperature side heat medium circuit 60 are not limited to those disclosed in the above embodiments.

[0304] In the above embodiments, examples of using ethylene glycol aqueous solution as the high-temperature side heat medium and the low-temperature side heat medium have been described, but the embodiments are not limited thereto. For example, solutions containing dimethyl polysiloxane or nanofluids, aqueous liquid media containing antifreeze or alcohol, or liquid media containing oil may also be used.

[0305] In the above embodiments, the mounting of the receiver assembly 30 to the vehicle is not mentioned, but it is sufficient to provide a fixing part for fixing to the vehicle, which is the object to be installed, on either the receiver section 15 or the switching section block 31. For example, the fixing part may not be provided on the receiver section 15 and the pressure reducing section block 32, but the fixing part (specifically, bolt holes) may be provided on the switching section block 31. As a result, heat damage can be further suppressed.

[0306] The technical means disclosed in the above embodiments can be appropriately combined within the scope of implementation. For example, if the receiver assembly 30 with a deceleration refrigerant passage 34 described in the fourth embodiment is used together with the collision plate 33 described in the first embodiment, the gas-liquid separation performance of the receiver section 15 can be further improved.

[0307] Although the invention has been described with reference to embodiments, it should be understood that the invention is not limited to those embodiments or structures. The invention also includes various modifications and variations within the same scope. Furthermore, various combinations, methods, and even other combinations and methods comprising only one element, or more than one element, also fall within the scope and spirit of the invention.

Claims

1. A refrigeration cycle device, characterized in that, have: The compressor compresses and discharges the refrigerant; A heat dissipation section that dissipates heat from the refrigerant discharged from the compressor; An outdoor heat exchange unit that allows the refrigerant to exchange heat with the outside air; A receiver-side pressure reduction section that reduces the pressure of the refrigerant; The receiver section performs gas-liquid separation on the refrigerant flowing out from the receiver-side pressure reducing section and stores the remaining refrigerant in the cycle; An evaporator-side pressure reduction section reduces the pressure of the refrigerant. An evaporator section, which evaporates the refrigerant whose pressure has been reduced by the pressure-reducing section on the evaporator side; and The refrigerant circuit switching unit switches the refrigerant circuit. The refrigerant circuit switching unit is configured to switch between the first circuit and the second circuit. The first circuit allows the refrigerant flowing from the outdoor heat exchange section to flow into the receiver-side pressure reducing section, allows the refrigerant flowing from the receiver section to flow into the evaporator-side pressure reducing section, and allows the refrigerant, whose pressure has been reduced by the evaporator-side pressure reducing section, to flow into the evaporator. The second circuit allows the refrigerant flowing from the heat dissipation section to flow into the receiver-side pressure reducing section, allows the refrigerant flowing from the receiver section to flow into the evaporator-side pressure reducing section, and allows the refrigerant whose pressure has been reduced by the evaporator-side pressure reducing section to flow into the evaporator. The refrigeration cycle device also includes: A deceleration section that reduces the flow rate of the refrigerant flowing into the receiver section due to pressure reduction by the pressure reduction section on the receiver side; Pressure reducing block, which is used for mounting the receiver-side pressure reducing section; and A switching unit block is provided for mounting the refrigerant circuit switching unit. The switching section block, the pressure reducing section block, and the receiver section are formed from different components. The switching unit block, the pressure reducing unit block, the receiver unit, and the deceleration unit are assembled into one unit.

2. The refrigeration cycle device according to claim 1, characterized in that, The switching block, the pressure reducing block, and the receiver are assembled together in such a manner that the switching block contacts the pressure reducing block, the pressure reducing block contacts the receiver, and the switching block and the receiver are not in contact.

3. The refrigeration cycle device according to claim 1 or 2, characterized in that, The deceleration section is disposed inside the receiver section and is formed of a plate-shaped member having a collision section for the refrigerant that has been depressurized by the depressurization section on the receiver side to collide with it.

4. The refrigeration cycle device according to claim 3, characterized in that, The plate-shaped component has a connecting portion, which forms a through hole that extends through both the inside and outside of the plate.

5. The refrigeration cycle device according to claim 4, characterized in that, Multiple through holes are provided. When the number of through holes is defined as N, and the total opening area of ​​the plurality of through holes is defined as SA, the dimensionless parameter P1, which is related to the amount of movement of the refrigerant through the through holes, is set to a predetermined reference value or lower. The dimensionless parameter P1 is defined by the following formula: P1=(Gr / N) / (ρ×V0×R0 2 )×(Gr / SA / ρ) / V0 Gr: Refrigerant flow rate in the receiver section, in mass flow rate: kg / s; ρ: Density of liquid refrigerant, in kg / m³ 3 ; V0: The flow rate of the liquid refrigerant flowing out of the receiver section, in m / s; R0: The equivalent diameter of the refrigerant passage for the liquid refrigerant flowing from the receiver section, in meters.

6. The refrigeration cycle device according to claim 1 or 2, characterized in that, The deceleration section is formed by a deceleration refrigerant passage that reverses the flow direction of the refrigerant flowing into the receiver section after being depressurized by the receiver-side depressurization section.

7. The refrigeration cycle device according to claim 6, characterized in that, The refrigerant passage for deceleration causes the flow direction of the refrigerant flowing into the receiver section after being depressurized by the receiver-side depressurization section to be redirected in the direction of colliding with the side wall of the receiver section.

8. The refrigeration cycle device according to claim 6, characterized in that, It includes a pressure-reducing block for mounting the pressure-reducing section on the receiver side. The refrigerant passage for deceleration is formed in the pressure reducing section block.

9. The refrigeration cycle device according to claim 1 or 2, characterized in that, It has a secondary chamber that stores liquid refrigerant flowing out from the heat dissipation section.

10. The refrigeration cycle device according to claim 9, characterized in that, When the refrigerant circuit switching unit switches to the second circuit, the dryness of the refrigerant flowing into the auxiliary box is lower than that of the refrigerant flowing into the auxiliary box when the refrigerant circuit switching unit switches to the first circuit.

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