KR102020930B1 - Refrigerant circuit, particularly for vehicles comprising electric or hybrid power train and method for operating the refrigerant circuit - Google Patents

Abstract

Refrigerant circuits, in particular vehicles for electric or hybrid powertrains including hybrid powertrains and methods of operating said refrigerant circuits
The present invention relates to a refrigerant circuit, in particular a refrigerant circuit for vehicles comprising an electric or hybrid powertrain, in which the condenser (3), the expansion valve (5), the separator (6) as a medium pressure cylinder, the expansion valve (7) in the refrigerant flow direction. ) Are arranged to be connected in series, and then, the battery cooler 11 and the air cooler 12 are arranged to be connected in parallel so that the main compressor 1 and the secondary compressor 2 are arranged in wiring, and the main compressor The high pressure side of (1) is connected to the suction side of the secondary compressor (2) by the shut-off valve 18 and the multi-way valve 16 in the high pressure cable of the main compressor (1) and the main compressor (1) and The secondary compressors 2 can be connected in series or in parallel, and the separator 6 is connected on the gas side with the suction side of the secondary compressor 2.
The present invention also relates to a method of operating a refrigerant circuit.

Description

REFRIGERANT CIRCUIT, PARTICULARLY FOR VEHICLES COMPRISING ELECTRIC OR HYBRID POWER TRAIN AND METHOD FOR OPERATING THE REFRIGERANT CIRCUIT}

The present invention relates to a vehicle refrigerant circuit with a particularly high refrigeration capacity compared to a general refrigeration circuit. Refrigerant circuits can be used for vehicles including electric or hybrid powertrains. What is special about the refrigerant circuits according to the preamble of the present invention is that in electric or hybrid vehicles the cooling of the battery or accumulator and components and the cooling of the vehicle interior for further air conditioning are optimal in driving operation and charging operation of the batteries. Is necessary to reach the conditions of In particular, the need for rapid charging of the battery raises special requirements for the refrigeration system of the vehicle, since the optimal charging of the batteries depends on the cooling of the batteries during the charging process.

Refrigerant circuits for vehicles, including electric or hybrid powertrains, are known in the art in various designs. In the prior art, for example, US 2009/0317697 A1 is known for a vehicle refrigeration system with a bypass, which is suitable for providing battery cooling by means of a battery cooler. DE 103 13 850 A1 also shows a refrigerant circuit with two-stage compression for combined refrigeration system operation and heat pump operation. The refrigerant circuit is provided with two compressors connected in series to implement two-stage compression, and the circuit is also optimal for being able to implement the heat pump operation of the entire system.

The subject of the invention is a vehicle comprising an electric or hybrid powertrain, which is also suitable for optimally providing cold air to batteries and electronic components in driving operation and charging operation of batteries together with the task of generating cold air for air conditioning of the vehicle cabin. It is to provide a refrigerant circuit. The aim of the present invention is to achieve as many operational states as possible, such as driving operation, charging operation and heat pump operation by the connection of the components provided in the circuit.

The problem is solved by a refrigerant circuit and method having the features according to the independent claims. Embodiments are presented in the dependent claims.

The problem of the present invention is solved by a refrigerant circuit optimized especially for vehicles including electric or hybrid power trains. The refrigerant circuit is characterized by the arrangement of the following components in the refrigerant flow direction. The refrigerant first passes through a condenser, followed by an expansion valve, followed by a separator, also referred to as a medium pressure cylinder in two-stage operation, and a collector, refrigerant separator or receiver in one-stage operation, and an additional expansion valve. The components are arranged in series connection. The refrigerant then passes through heat exchangers that act as evaporators, ie battery coolers and air coolers arranged in parallel. The refrigerant is sucked by the main compressor as refrigerant vapor after passage of the battery cooler and the air cooler. In addition to the main compressor, a secondary compressor is provided in the refrigerant circuit. The main compressor and the secondary compressor are integrated into the circuit in parallel to each other, and the main compressor and the secondary compressor can be connected in parallel and in series by arranging behind the main compressor a disconnectable connection to the suction side of the secondary compressor. A shutoff valve is also provided in the high pressure cable of the main compressor and a multiway valve in the connection of the main compressor cable and the secondary compressor cable. Separators generally comprise an inlet for a liquid-gas-refrigerant mixture, and an outlet for gas and an outlet for liquid. The outlet of the gas separator is also called the gas side and is connected to the suction side of the secondary compressor.

Particularly preferably, the refrigerant circuits with the above-mentioned possibilities of parallel and series connection of the presented components and the main compressor and the secondary compressor are suitable for implementing various operating states for electric or hybrid vehicles, since the This is because several operating states can be implemented.

Preferably a shut-off valve is arranged in the connection of the suction side of the secondary compressor and the gas side of the separator.

Preferably, expansion valves are separately assigned to the battery cooler and the air cooler, respectively. Each heat exchanger can be controlled separately and regulated technically with the whole system and under consideration of the specific pressure loss of the heat exchanger.

Preferably an additional coolant circuit is formed, including a pump, a heat pump heat exchanger and a coolant-air-cooler, and the heat pump heat exchanger having an allotted expansion valve is used for the battery cooler and air cooler in the refrigerant circuit. Arranged in parallel. As a coolant, preferably water or a water-glycol-mixture can be used, the coolant-air-cooler is also a water-air-cooler. The coolant-air-cooler is also a low temperature heat exchanger or a high temperature heat exchanger in view of its use temperature range.

According to a particularly preferred design of the invention the further condenser is arranged to be selectively or cumulatively switchable in the coolant circuit and the refrigerant circuit by means of a multiway valve. The further condenser is arranged behind the condenser in the refrigerant flow direction in the refrigerant circuit.

A particularly preferred structural design of the circuit is achieved if the secondary compressor is formed to be integrated into the main compressor and thereby the main compressor is implemented as a two-stage compressor.

The problem of the present invention is also solved by the method of operation of the refrigerant circuit, in the traveling operation of the air conditioning mode, the refrigerant is first compressed in one-stage in the main compressor and then passed through the condenser under heat release and then in the expansion valve. It is reduced to medium pressure. The gaseous phase of the refrigerant in the separator is sucked by the main compressor, throttled into the suction line of the compressor according to the pressure level, or provided to the compressor corresponding to the pressure level, the liquid phase of the refrigerant being parallel in the air cooler and the battery cooler. Is evaporated and then sucked by the main compressor. In this mode the refrigerant circuit is operated in one stage and the secondary compressor is not activated. The refrigeration capacity of the refrigeration circuit thus connected corresponds to the general refrigeration capacity of the vehicle air conditioners. By not selectively depressurizing in front of the separator in a one-stage process, an expansion valve connected in front, with a complete passage cross section without throttling of the refrigerant, is incorporated.

Preferably the refrigerant is each separately depressurized by expansion valves assigned to separate heat exchangers in front of the air cooler and the battery cooler.

The problem of the invention is also solved by a method of operating the refrigerant circuit, in which the refrigerant is first compressed in two stages by the main compressor and the secondary compressor connected in series in the charging operation of the battery. The refrigerant then passes through the condenser under heat release and is then decompressed to medium pressure in the expansion valve. The gas phase of the refrigerant is sucked by the secondary compressor in this circuit and the liquid phase of the refrigerant is evaporated in the battery cooler and sucked by the main compressor. The air cooler is not activated in this operating mode of the only filling operation so that the total cooling capacity and the freezing capacity can be used for the filling operation and in particular the quick filling operation. Of course, under reduced cooling capacity, optional refrigeration capacity can be used for air conditioning in the vehicle interior.

Particularly preferably the heat dissipation of the refrigerant is supported by an additional condenser connected in series in the refrigerant circuit in addition to the condenser.

The problem of the present invention is solved by the method of operation of the refrigerant circuit, in the one-stage heat pump operation, the refrigerant is compressed in one-stage in the main compressor and then passes through the condenser under heat dissipation into the vehicle interior and in the expansion valve Reduced to medium pressure at. The gas phase of the refrigerant is sucked by the main compressor and the liquid phase of the refrigerant is evaporated in the heat pump heat exchanger and sucked by the main compressor to close the circuit. This mode of operation is particularly desirable when the heat demand is relatively low.

The problem of the present invention is also solved by a method of operating the refrigerant circuit, in which the refrigerant is compressed in the main compressor and the secondary compressor and thus in two stages in a two stage heat pump operation. The refrigerant then passes through the condenser under heat dissipation into the vehicle interior. In the expansion valve the refrigerant is reduced to medium pressure and the gas phase of the refrigerant is sucked by the secondary compressor. The liquid phase of the refrigerant is evaporated in parallel in the heat pump heat exchanger, ie in the air cooler and the battery cooler and sucked by the main compressor. In this way a particularly high proportion of heat is provided in the vehicle interior by means of a heat pump function.

In particular preferably the heat pump system according to the above-described variant is formed such that the heat absorption of the refrigerant in the heat pump heat exchanger is further from the coolant circuit, and the coolant circuit in the heat pump heat exchanger is thermally connected with the refrigerant circuit. In refrigeration system operation, the water-condenser in the coolant circuit is connected.

The above-described method is preferably formed by the additional heat transfer area being activated in particular in the charging operation of the battery for heat dissipation in the battery cooler.

The methods are preferably extended by further heat transfer areas for heat dissipation in the coolant-air-cooler, in particular being activated in the filling operation or by the use of other components due to the total area being unused.

Preferably the methods are complemented by implementing a temperature difference in which the additional heat transfer area for the heat dissipation in the condenser is driven by a higher pressure, the capacity of the condenser being activated or unchanged, especially in the filling operation.

Other individual details, features and advantages of embodiments of the invention are set forth in the following description of the embodiments with reference to the associated drawings.

1 shows a refrigerant circuit with two compressors,
2 is a refrigerant circuit with two compressors and a breakable medium medium pressure gas pipe;
3 is a refrigerant circuit in combination with a coolant circuit,
4 shows the function of the refrigerant circuit designed in two stages in the heat pump operation,
5 is a refrigerant circuit with a battery cooler at a medium pressure level, and
6 shows a refrigerant circuit with a battery cooler at low pressure levels and selective gas supply to low and medium pressure levels.

1 shows a design of a refrigerant circuit showing the basic principle with the components involved. The main compressor 1 and the secondary compressor 2 are integrated into the refrigerant circuit by means of shut-off valves 16, 18 for series connection operation and for parallel connection operation. The refrigerant circuit comprises a condenser 3 at a high pressure level, subsequently an expansion valve 5 and a separator 6 in series connection in the flow direction. When the two-stage operation is operated at the medium pressure level of the refrigerant, the separator 6 is also called a medium pressure cylinder. Once compressed in one-stage, the separator 6 in its function is reduced to a collector for liquid refrigerant after the first expansion stage by the expansion valve 5 or it runs in a cross section in which the expansion valve 5 is fully open and The expansion is implemented by the expansion valve 7. At medium or high pressure the refrigerant vapor phase from the separator 6 reaches the suction side of the secondary compressor 2 via a pipe. The liquid refrigerant from the separator 6 is reduced to low pressure in the expansion valve 7 and then distributed in parallel to the loads, namely the battery cooler 11 and the air cooler 12. The evaporated refrigerant from the heat exchangers is provided together on the suction side of the main compressor 1. As will be described in more detail below, when the circuit is operated in one-stage the shutoff valve 18 for the high pressure gas of the main compressor 1 is opened and the compressed refrigerant arrives directly into the condenser 3. When the system is operated in series connection by the compressors 1, 2, the shutoff valve 18 for the high pressure gas of the main compressor 1 is closed and the refrigerant vapor from the separator 6 is connected to the connecting pipe and the multiway valve ( 16) to the suction side of the secondary compressor 2, which is compressed by the secondary compressor to high pressure and reaches into the condenser 3. As an alternative method of operation, the refrigerant circuit can be operated in parallel by the compressors 1, 2. The high pressure gas shut-off valve 18 of the main compressor 1 is opened and the parallel cable for the secondary compressor 2 has a multi-way valve 16 in the refrigerant circuit for parallel flow of refrigerant to the suction side of the secondary compressor 2. Is connected to achieve.

In FIG. 2, the components in accordance with FIG. 1 are characterized in that the gaseous phase from the separator 6 reaches the intake side of the secondary compressor 2 via a connecting pipe, in which a shutoff valve 17 for heavy pressure gas is implemented. It is shown again with special points.

By the refrigerant circuit shown, the compressors can be switched from parallel mode to series mode. Preferably the compressors are connected in series. The advantages of the two designs of series and parallel connection are the separation of the liquid phase of the refrigerant and the delivery of the gas phase of the refrigerant from the distributor 6 directly to the corresponding compressor, whereby minimization of pressure loss in the evaporator is achieved. Thus, the distribution of the liquid and gaseous phase in the evaporator is improved when less or no gas phase is reached into the evaporator. When the compressors are connected in series, the first expansion valve is responsible for the main depressurization. In addition, the flow of gaseous phase can be controlled by the shutoff valve 17.

3 is a combination of a refrigerant circuit and a coolant circuit, and the refrigerant circuit of FIGS. 1 and 2 extends to include a heat pump heat exchanger 10 with an associated expansion valve 9. In addition, an additional condenser 4 is provided for the thermal connection of the coolant circuit and the refrigerant circuit, which is implemented as a water-condenser. The further condenser 4 is integrated into the coolant circuit, which is driven by the pump 13 of the coolant circuit. The flow paths of the parallel cables of the coolant circuit are controlled by the multiway valve 15 of the coolant circuit. The first flow path goes from the pump 13 through the multiway valve 15 to the heat pump heat exchanger 10 and then through the low temperature heat exchanger, also called coolant-air-cooler 14, to the pump 13. do. The parallel cable is shown to proceed from the multiway valve 15 of the coolant circuit to the further condenser 4 and then to the coolant-air-cooler 14. A coolant circuit is required for the connection of the refrigerant circuit for the heat pump operation and the two circuits are thermally connected by an additional condenser 4 and a heat pump heat exchanger 10.

The concept of the invention is particularly evident by the circuit shown in Fig. 3, in which two compression stages and thus medium pressure levels are formed in the refrigerant circuit. The two compression stages are preferably implemented by two separate compressors 1, 2, in particular being able to operate the two compressors in series connection and in parallel connection. The system preferably includes the use of a water-condenser 4 having at least the same or increased capacity as a conventional air-condenser. Components 4, 8, 11, 14 are particularly relevant for the increased capacity. The components are designed with different capacities in normal operation of the system, ie cooling operation, heat pump operation or charging operations on an increase in refrigerant flow rate. It is particularly difficult to give a flow rate of refrigerant sufficient to carry the oil back to the compressor when the capacity is low. In the filling operation, the flow rate and thus the flow rate of the refrigerant must be large, and correspondingly the free flow cross section must be large, thereby avoiding pressure loss in critical areas. Heat exchangers also need a larger area to deliver the corresponding capacity. In particular, the water and condenser 4, the battery cooler 11 and the coolant-air-cooler 14 are in focus, and the medium and heat exchanger in which the heat exchanger 14 with a slightly larger heat transfer area is placed in the heat transfer section. The high thermal permeability of the material of (4) meets the corresponding capacity requirements and does not pose a problem to address in terms of oil transportation. Even more important are the battery cooler 11 and the coolant-air-cooler 14. In the case of the battery cooler 11 optionally heat transfer ducts are already provided in the heat exchanger, which are activated by switchable valves, i.e. self-regulating valves with spring force, upon corresponding capacity requirements. The valves are opened at corresponding pressure differentials. The coolant-air-heat exchanger 14 is dimensioned to such an extent that the heat exchanger takes charge of the additional heat source and can release corresponding capacities to the surroundings. The above capacities are not necessary in the charging operation and can be provided completely in the charging process. When charging in winter, the vehicle interior is heated.

The heat transfer area is reduced overall because additional areas are connected only under special operating conditions. The flow rate in the refrigerant circuit preferably increases with the parameter.

By operating the water-condenser 4 with a higher temperature difference at the same external dimensions, higher heat energy can be transferred in relation to the installation volume of the heat exchanger 4.

The two compressors 1, 2 comprise an oil separator / muffler connected to the front on the suction side. Typically the oil separator is arranged on the high pressure side. For reasons of distribution the two compressors 1 and 2 must be connected to an oil separator. The muffler is formed on the high pressure side for reasons of noise emission. In general, it is divided into two operating cycles. In the cooling operation and the heating operation, the refrigerant circuit can be operated by one compressor in one stage. Energy and technical (constant distribution of refrigerant in the battery cooler) are of course presented from the possibility of two-stage compression and refrigerant separation in medium pressure cylinders for this use. Thus, the oil separator / muffler is optionally provided. In the filling operation all the two compressors are operated in a two-stage or one-stage process.

4 shows a heat pump circuit of a refrigerant circuit in which the main compressor 1 and the secondary compressor 2 are connected in series in two stages. The refrigerant is condensed in the condenser 3, depressurized in the expansion valve 5 and the gas phase is separated from the liquid phase of the refrigerant in the subsequent separator 6. The gas phase is supplied to the suction side of the secondary compressor 2 at medium pressure, the liquid phase is distributed in parallel to the heat pump heat exchanger 10, the battery cooler 11 and the air cooler 12, and the expansion valves 7, 8 and 9 are assigned to heat exchangers respectively. The refrigerant evaporated in the heat exchangers 10, 11, 12 is finally integrated and supplied to the suction side of the main compressor 1.

An unshown variant of the heat pump circuit is the arrangement of two condensers. The first condenser, i.e. the vehicle interior heater, is installed in the air conditioner of the vehicle. The second condenser is a general air-condenser, which can be embodied as a water-condenser according to a preferred design. The illustrated embodiment with three heat exchangers 10, 11, 12 in the refrigerant system for evaporation of the refrigerant can naturally be extended by complex evaporator arrangements depending on the application. It only depends on the position of the thermostatic expansion valve, each installed with a shutoff function. As an alternative to FIG. 4, the heat pump circuit can also be implemented in one stage, with the main compressor 1 directly supporting the condenser 3 and the gas phase from the separator being connected to the suction side of the main compressor 1. Supplied. Heat is supplied from the coolant circuit by heat pump heat exchanger 10.

In the heat pump circuit, the condenser 3 dissipates heat into the interior of the vehicle. The advantage of the circuit guide shown is that low icing is achieved in the corresponding heat transfers and that a good storage capacity of the system is given. In addition, the heat of the battery cooler 11, the air cooler 12 and the heat pump heat exchanger 10 is made available for the heat pump. As an alternative to the heat pump circuit implemented in one-stage, the expansion valve 5 runs in a fully open cross-section so that it is compressed only by the main compressor 1 and the secondary compressor 2 does not operate in this operating position. Particularly preferably, the battery cooler heat in the circuit is used for heating the vehicle interior.

5 shows a modified refrigerant circuit, in particular the battery cooler 11 is directly supplied by the pump 19 with liquid refrigerant from the separator 6 and the refrigerant to be evaporated to this pressure level is separated from the separator 6. The weather will be provided again. The air coolers 12 are supplied with the refrigerant in parallel to the battery cooler 11 but the evaporated refrigerant is supplied to the suction side of the main compressor 1. Expansion valves 7 are assigned to the air coolers 12, respectively. The second compression stage is implemented by the secondary compressor 2, whereby a refrigerant is provided to the condenser 3. In particular in this variant for battery cooling the pressure levels are low and medium. The advantage is that the compressor can also operate as an evaporator in which the battery cooler 11 is completely full without being loaded by liquid shocks. The advantage is the level of evaporation temperature which remains exactly constant over the total heat transfer area.

6 shows an alternative to the design according to FIG. 5, wherein the battery cooler 11 is supplied with liquid refrigerant from the separator 6 in parallel to the air coolers 12. The refrigerant liquid from the separator is depressurized in the expansion valve 8 and adjusted to the corresponding pressure level. Similarly, expansion valves 7 are assigned to the air coolers 12. The refrigerant vapor from the battery cooler 11 reaches the suction side of the main compressor 1 or the suction side of the secondary compressor 2 by the multiway valve 20 depending on the pressure level. The battery cooler 11 with the expansion valve 8 is integrated into the refrigerant circuit by the multiway valve 20 and the refrigerant flow rate from the battery cooler 11 by the multiway valve 20 is the medium pressure flow rate or the low pressure of the refrigerant. Integration into the flow rate is achieved.

The refrigerant circuits shown may further comprise an internal heat exchanger between the low and high pressure side or between the medium and high pressure side. Irreversible expansion units can also be replaced by work performing expansion units. These two variants are provided for improving the efficiency of the circuits.

1 main compressor
2 secondary compressor
3 condenser
4 additional condenser, water-condenser, heat exchanger
5 medium pressure expansion valve
6 separator
7 low pressure expansion valve
8 low pressure expansion valve
9 low pressure expansion valve
10 heat pump heat exchanger, heat exchanger
11 battery cooler, electronic cooler, heat exchanger
12 air cooler, vehicle indoor evaporator, heat exchanger
13 Pump of Refrigerant Circuit
14 Coolant-air-cooler
15 Multi-way Valve in Coolant Circuit
16 Refrigerant Circuit Multi-way Valve, Shut-off Valve
17 isolating valve for medium pressure gas
18 High pressure gas shutoff valve on the main compressor
19 refrigerant pump
Multi-way valve on 20 battery cooler circuit branch

Claims (16)

As the refrigerant circuit, the condenser 3, the expansion valve 5, the separator 6 as the medium pressure cylinder, the expansion valve 7 are arranged in series connection in the refrigerant flow direction, and then the battery cooler 11 and the air cooler ( By arranging 12 in parallel, the main compressor 1 and the secondary compressor 2 are arranged in parallel,
The high pressure side of the main compressor (1) comprises an intermediate flow path connected to the suction side of the secondary compressor (2),
Refrigerant sequentially moves the main compressor 1 and the secondary compressor 2 by a shutoff valve 18 disposed on the high pressure side of the main compressor 1 and a multiway valve 16 disposed in the intermediate flow path. And the separator (6) is connected to the intermediate passage on the gas side and connected to the suction side of the secondary compressor (2). 2. Refrigerant circuit according to claim 1, characterized in that a shutoff valve (17) is provided in a connection between the suction side of the secondary compressor (2) and the gas side of the separator (6). The refrigerant circuit according to claim 1, characterized in that an expansion valve (7, 8) is separately assigned to the battery cooler (11) and the air cooler (12). An additional coolant circuit is formed, the additional coolant circuit comprising a pump (13), a heat pump heat exchanger (10), and a coolant-air-cooler (14), wherein the heat pump heat exchanger ( The heat pump heat exchanger 10 comprising an expansion valve 9 upstream of the refrigerant 10 is arranged in parallel to the battery cooler 11 and the air cooler 12 in the refrigerant circuit. Circuit. 5. A further condenser (4) according to claim 4, wherein an additional condenser (4) is arranged in the coolant circuit so as to be selectively or cumulatively switchable by the multi-way valve (15). A refrigerant circuit, characterized in that it is arranged behind the condenser (3) in the direction of refrigerant flow. The refrigerant circuit according to claim 1, wherein the secondary compressor (2) is formed to be integrated into the main compressor (1) and the main compressor (1) is implemented as a two-stage compressor. In the method of operating the refrigerant circuit according to any one of claims 1 to 6, the refrigerant in the running operation of the air conditioner mode
Compressed in one-stage within the main compressor (1),
Then through the condenser 3 under heat dissipation,
Pressure reduction in medium pressure in the expansion valve (5), and
The liquid phase of the refrigerant is evaporated in parallel in the air cooler (12) and the battery cooler (11) and is sucked by the main compressor (1) together with the gas phase from the separator (6). How the circuit works. 8. A method according to claim 7, wherein the refrigerant is separately depressurized by expansion valves (7, 8) in front of the air cooler (12) and the battery cooler (11). The method of claim 7, wherein the refrigerant in the charging operation of the batteries
Compressed in two stages in the main compressor (1) and the secondary compressor (2),
Then through the condenser 3 under heat dissipation,
Pressure reduction in medium pressure in the expansion valve (5),
The gaseous phase of the refrigerant is sucked by the secondary compressor (2), and
The liquid phase of the refrigerant is evaporated in the battery cooler (11) and sucked by the main compressor (11). 10. A method according to claim 9, characterized in that the heat dissipation of the refrigerant takes place in an additional condenser (4) subsequently connected in series with the refrigerant circuit in addition to the condenser (3). 10. The method of claim 9, wherein in the one-stage heat pump operation the refrigerant is
Compressed in one-stage within the main compressor (1),
Then through the condenser 3 under heat dissipation into the vehicle interior,
Pressure reduction in medium pressure in the expansion valve (5),
The gaseous phase of the refrigerant is sucked by the main compressor (1), and
The liquid phase of the refrigerant is evaporated in the heat pump heat exchanger (10) and sucked by the main compressor (1). The method of claim 11, wherein in the two-stage heat pump operation the refrigerant is
Compressed in two stages in the main compressor (1) and the secondary compressor (2),
Then through the condenser 3 under heat dissipation into the vehicle interior,
Pressure reduction in medium pressure in the expansion valve (5),
The gaseous phase of the refrigerant is sucked by the secondary compressor (2), and
The liquid phase of the refrigerant is evaporated in parallel in the heat pump heat exchanger 10, the air cooler 12, and the battery cooler 11 and sucked by the main compressor 1. How the circuit works. 13. The method of claim 12, wherein the heat absorption of the refrigerant in the heat pump heat exchanger (10) is further from the coolant circuit in the heat pump heat exchanger (10). delete delete delete

Images