DE102013204188A1 - Refrigerant circuit - Google Patents

Abstract

The invention relates to a refrigerant circuit comprising a compressor (1), a condenser (2), an external heat exchanger (6) and a first evaporator (8), from which the refrigerant is returned to the compressor (1), one by A bypass line (3b) that can be shut off and released is provided, which bypasses the first evaporator (8) and connects the outdoor heat exchanger (6) to the compressor (1), characterized in that a second evaporator (11) is integrated in the refrigerant circuit is connected in parallel to the first evaporator (8).

Description

The invention relates to a refrigerant circuit with a compressor, a condenser, an external heat exchanger and an evaporator, wherein the refrigerant circuit can operate in the cooling mode and by bypassing the evaporator through a bypass line in heat pump mode.

Out DE 696 29 881 T2 is a refrigerant circuit with a phase separator known, which is arranged between the condenser and an outdoor heat exchanger, which operates in the cooling mode of the refrigerant circuit in addition to the condenser as a condenser and heat pump operation as an evaporator. By supplying vaporous refrigerant from the phase separator to the compressor at a medium pressure, the compressor in this refrigerant circuit is referred to as a two-stage compressor which compresses the vapor refrigerant from the evaporator at low pressure and the vapor refrigerant from the phase separator at medium pressure.

The object of the invention is to design a refrigerant circuit of the type specified in such a way that it can take on additional functions and the efficiency is increased in heat pump operation.

According to the invention, this object is achieved by a refrigerant circuit, comprising a compressor, a condenser, an external heat exchanger and a first evaporator, from which the refrigerant is returned to the compressor, wherein a bypassable by a valve bypass line is provided which bypasses the first evaporator and the External heat exchanger connects to the compressor, and wherein in the refrigerant circuit, a second evaporator is integrated, which is connected in parallel to the first evaporator.

By providing a second evaporator, in the cooling mode, for example, the battery of a motor vehicle provided with an electric motor can be cooled by the second evaporator, while in heat pump operation, by means of the second evaporator, the waste heat from electrical components of the motor vehicle such as battery, electric motor and the like are used as a heat source can improve efficiency in heat pump operation.

The second evaporator may be in heat exchange with a fluid, which is typically water or a water-glycol mixture. Such a standing in water with heat exchanger evaporator is referred to in motor vehicles as a chiller. The second evaporator can also be in heat exchange with air.

According to a further embodiment, the second evaporator may also be directly in heat exchange with a component of a vehicle, for example the battery of an electric vehicle without the interposition of a fluid.

It can be provided in the refrigerant circuit, a two-stage compression, wherein the condenser is followed by a phase separator, which separates the vapor and liquid refrigerant, and the vapor refrigerant in the medium pressure region of the compressor and the liquid refrigerant is supplied to the outdoor heat exchanger.

According to a first embodiment of the invention, the second evaporator or chiller can be connected downstream of the outdoor heat exchanger in series.

Preferably, according to a second embodiment, the second evaporator is connected in parallel to the outdoor heat exchanger.

As a result, although a slightly lower efficiency (COP) is achieved in the heat pump operation than in the first embodiment with series connection, but one gets a simpler and more cost-effective design of the entire refrigerant circuit, because to be provided in the series circuit complex line design between outdoor heat exchanger and the second evaporator including the required valves deleted. Overall, this is a great practical advantage achieved by simple and inexpensive design against only a small loss of performance over a series connection.

Advantageously, the control of at least one valve switches between series connection and parallel connection.

In the parallel connection of the two evaporators, the refrigerant line is divided downstream of the condenser in a primary circuit with the outdoor heat exchanger and in a secondary circuit with the second evaporator, the two circles are combined again between the outdoor heat exchanger and the second evaporator.

According to a further embodiment, a branch line is branched off from the refrigerant line to the condenser in a primary circuit and a secondary circuit, which is connected to the refrigerant line before the second evaporator and in which a valve for shutting off and releasing is arranged.

In the series connection of the second evaporator and the outdoor heat exchanger, the connecting section between the outdoor heat exchanger and the second evaporator is expediently designed such that the associated line volume as small as possible. Advantageously, the line volume is less than 30 or 20%, preferably less than 10% of the usable storage volume of a rechargeable battery designed.

In parallel connection of the second evaporator and the outdoor heat exchanger, the connection between the outdoor heat exchanger and branch to the second evaporator is designed with a considerably larger cross-section than between branching to the second evaporator and branching to the first evaporator in order to achieve optimum operation.

In this case, the connection path between the outdoor heat exchanger and the branch to the second evaporator is preferably designed to be considerably shorter than between the branch to the second evaporator and the branch to the first evaporator.

It is advantageous if each of the parallel evaporators in each case an expansion or control valve is connected upstream and the two evaporators an accumulator downstream, one of the valves is independent of the conditions of the refrigerant circuit is adjustable, so that the valve downstream of this evaporator regardless Refrigerant circuit can be controlled.

According to a development of the invention, a refrigerant circuit with a compressor, a condenser and at least two evaporators connected in parallel is provided, which are each controllable by a separate valve, wherein at least one of the valves is independent of regulated parameters of the refrigerant circuit is adjustable and the two evaporators Accumulator is connected downstream. In this case, a pure refrigerant circuit without heat pump function is formed.

Due to the independent of the parameters to be controlled of the refrigerant circuit adjustable valve z. B. the water temperature of a standing with the downstream evaporator in heat exchange cooling water circuit can be set exactly without having to take into account the conditions of the refrigerant circuit consideration.

In an embodiment in which z. B. the battery of an electric vehicle is cooled directly by the refrigerant and in addition a chiller is used for waste heat recovery, in addition to the two parallel evaporators also another evaporator may be provided, which is connected in parallel to the two evaporators.

The invention will be explained in more detail for example with reference to the drawing. Show it

1 a per se known refrigerant circuit with phase separator and two-stage compression,

2 a schematic representation of the refrigerant circuit with series-connected chiller,

3 schematically the primary refrigerant circuit with a secondary pitch with chiller parallel to the primary refrigerant circuit with two-stage compression,

4 in the representation of the refrigerant circuit after 1 various circuits of the refrigerant circuit, and

5 another embodiment of the invention with parallel evaporators.

In the following 1 to 4 Although a refrigerant circuit is shown with two-stage compression, the embodiment of the invention with two parallel evaporators in the refrigerant circuit is not limited to two-stage compression, as will be explained below.

1 shows a refrigeration cycle with two-stage compression, wherein compressed, vapor refrigerant from a compressor 1 to a capacitor 2 flows, from which a refrigerant pipe 3 to a throttle device or an expansion valve 4 leads, by its degree of opening a phase separator 5 can be controlled, the liquid and vapor refrigerant separates. Vaporous refrigerant is supplied via a refrigerant line 3a in the medium pressure area of the compressor 1 supplied while liquid refrigerant through the refrigerant line 3 an outdoor heat exchanger 6 is fed, from which the refrigerant line 3 to an expansion valve 7 and an evaporator 8th leads, which has an accumulator 9 with the compressor 1 connected is. A bypass line 3b in which a two-way valve 10 is arranged bypasses the expansion valve 7 and the evaporator 8th ,

In heat pump mode, the capacitor forms 2 a heat-emitting heater, wherein the outdoor heat exchanger 6 works as an evaporator. This is done by closing the expansion valve 7 and opening the two-way valve 10 in the bypass line 3b that of the outdoor heat exchanger 6 coming, mainly vaporous refrigerant to the compressor 1 over the accumulator 9 fed directly.

During cooling operation of the refrigerant circuit, the phase separator 5 by fully opening the expansion valve 4 flows through without phase separation, the outdoor heat exchanger 6 works as a primary condenser. The two-way valve 10 is closed, so the liquid High pressure refrigerant in the expansion valve 7 relaxed and in the evaporator 8th is evaporated.

In that regard, the structure of the refrigerant circuit is after 1 and its function state of the art.

According to the invention in the refrigerant circuit of 1 a second, acting as an evaporator heat exchanger arranged in parallel to the first evaporator of the refrigerant circuit, by means of the one hand in heat pump operation to improve the efficiency of a heat source, such as the battery of a motor vehicle provided with an electric drive is used, while on the other hand in the cooling mode called chiller Heat exchanger, for example, for cooling the battery can be preferably used via a water cycle.

If the outdoor heat exchanger 6 As an evaporator, it tends to be at the outlet of the outdoor heat exchanger due to the relatively low temperature of the refrigerant 6 at the refrigerant circuit after 1 to icing. The icing tendency is due to the integration of the chiller 11 decreases because the outlet temperature at the outdoor heat exchanger 6 is increased.

2 shows the arrangement of a chiller 11 in a simplified reproduced refrigerant circuit of the 1 in a series connection in the refrigerant line 3 the outdoor heat exchanger 6 immediately downstream. This results in a high efficiency in heat pump operation, as shown in the schematic diagram in FIG 2a can be derived, however, the wiring and design between outdoor heat exchanger 6 and chillers 11 must meet several requirements. In cooling mode (A / C mode) gives the outdoor heat exchanger 6 as a condenser liquid refrigerant from and in heat pump mode (HP mode) as an evaporator vapor refrigerant. The chiller 11 always works as an evaporator. This results in the problem that in heat pump operation with vaporous refrigerant, the pressure loss between outdoor heat exchanger 6 and chillers 11 must be kept low, so ideally a large cable cross-section is required. In cooling mode is located at the exit of the outdoor heat exchanger 6 liquid refrigerant before. In order not to have to increase the filling amount of the refrigerant in the refrigerant circuit, the subsequent line volume must be as small as possible. To meet both requirements, the line section from the outdoor heat exchanger 6 until the diversion of the evaporator 8th have a relatively large cross-section and be relatively short, with cross-section and length in relation to the other line section to chiller 11 you can see. This may possibly be difficult because of the space available in a vehicle only limited space.

Advantageously, the chiller 11 in a partial circle parallel to the outdoor heat exchanger 6 arranged like this in 3 is shown schematically.

In this designated as a secondary refrigerant circuit pitch circle branches from the condenser 2 incoming refrigerant line at a branching point 3.1 in the phase separator 5 leading refrigerant line 3 and in a refrigerant line 30 leading to the chiller 11 leads. Between outdoor heat exchanger 6 and chillers 11 become the two refrigerant pipes 3 and 30 at the junction 3.2 merged to the compressor 1 leading refrigerant line. For the sake of clarity, in 2 and 3 usually the compressor 1 upstream accumulator 9 and other elements of the refrigerant circuit omitted.

In the circle 30 Only one-stage compression of the in this sub-circle from the branching point takes place 3.1 inflowing refrigerant in contrast to the two-stage compression in the primary circuit in this embodiment 3 ,

Through this parallel connection of the chiller 11 relative to the outdoor heat exchanger 6 in 3 Although a slightly lower efficiency in heat pump operation compared to the series connection after 2 achieved, as can be seen from the schematic diagram in 3a However, the line design is not subject to the conflicting requirements for the cooling and heat pump operation, previously in connection with the series circuit of 2 has been described.

Also in this parallel circuit of 3 will be a higher temperature at the outlet of the outdoor heat exchanger 6 towards the refrigerant circuit 1 reached, like 3a shows. The outlet temperature of the outdoor heat exchanger 6 can typically after about 2 ° -6 ° K compared to the refrigerant circuit 1 be increased so that the tendency to icing is less.

In 3a is the circle 30 corresponding lines represented by a dashed line.

Another benefit of parallel switching after 3 is that the performance of the chiller 11 through an upstream, in 3 unillustrated expansion valve is better regulated than in the series connection after 2 , In parallel connection to 3 is the flow and Control of the chiller 11 regardless of the flow and control of the outdoor heat exchanger 6 ,

The pressure loss at the outlet of the outdoor heat exchanger 6 can also be connected in parallel 3 be kept low compared to the refrigerant circuit after 1 , Depending on the respective operating point results in a typically in a range of about 0.2-0.6 bar lower pressure loss under otherwise identical conditions, so that total compared 1 An increase in efficiency (COP) by about 25% can be achieved.

By a chiller 11 upstream expansion valve 11.1 ( 4 ) finally results in a simple control of the water-side performance of the refrigerant circuit, because the overheating of the refrigerant must be taken into account only to a lesser extent. A possibly excessive overheating is caused by the accumulator 9 in conjunction with the outdoor heat exchanger 6 compensated.

The expansion valve 11.1 can be controlled independently of the refrigerant circuit in a wide range, eg. B., the water outlet temperature of the chiller 11 by controlling the valve 11.1 be managed.

Due to the parallel connection to 3 results in a relatively simple integration of a chiller in a refrigerant circuit with or without two-stage compression, the chiller 11 can be operated in the cooling operation as an evaporator, for example, for cooling the battery of a motor vehicle provided with an electric drive and in heat pump operation to increase the efficiency of the waste heat of, for example, electrical components of the motor vehicle can be exploited.

4 shows the integration of the second evaporator or chiller 11 in the in 1 reproduced primary circuit, wherein the same reference numerals are used for the same or corresponding elements as in the 1 to 3 ,

In 4 is opposite 1 the parallel to the first evaporator 8th arranged second evaporator or chiller 11 in a bypass line 3c between the first evaporator 8th and bypass line 3b arranged to allow the refrigerant line between outdoor heat exchanger 6 and turn off to the chiller 11 can be kept as short as possible.

But it is also possible, the bypass line 3c with chiller 11 to the right of the evaporator 8th in 4 to arrange.

The chiller 11 is in 4 reproduced as traversed by refrigerant heat exchanger, which is in heat exchange with a coolant, usually water or a water-glycol mixture.

On the exit side of the condenser 2 branches 3.1 the line 30 in 3 corresponding line 30 from the refrigerant line 3 off, via a shut-off valve 14 between outdoor heat exchanger 6 and expansion valve 11.1 at the junction 03.03 with the refrigerant line 3 connected is. at 15 is a check valve or an actively controlled valve between branch point 03.03 and outdoor heat exchanger 6 intended.

4a corresponds to the parallel operation of 3 or a mode of operation 1 ,

4b corresponds to the series connection after 2 or a mode of operation 2 , These two operating modes refer to a heat pump operation (HP mode)

4c corresponds to a cooling mode (A / C mode) or an operating mode 3 ,

In the circuit after 4a (Heat pump operation with evaporators connected in parallel according to operating mode 1 ) is the valve 14 open and that of the capacitor 2 incoming mass flow will be at the branching point 3.1 in the the refrigerant line 3 flowing through partial flow and the refrigerant line 30 divided by flowing partial flow, as shown by arrows. The two-way valve 10 in the bypass line 3b is open and the evaporator 8th is through the closed control valve 7 not in use. The check valve 15 is closed as indicated by a broken line at 3.4 in 4a is indicated. The refrigerant flows from the chiller 11 to the connection point 3.2 with the from the outdoor heat exchanger 6 coming line and over the accumulator 9 to the compressor 1 , optionally a two-stage compaction in conjunction with the 3a injected refrigerant performs.

It should be noted that the HP mode in 4a with and without phase separator 5 is possible. Instead of omitting the phase separator 5 and the branch line 3a can the phase separator 5 Also be switched so that it performs no phase separation and the refrigerant performs the phase separator 5 flows through without interference.

The control or expansion valve 4 controls the high pressure in the refrigerant line 3 or the subcooling after the condenser or condenser 2 and thus the entry state of the refrigerant in both evaporators 6 and 11 ,

The accumulator 9 provides both the exit state (constant steam content) to the outdoor heat exchanger 6 as well as after the chiller 11 one.

The control valve 11.1 is no longer needed for controlling the chiller inlet and outlet conditions.

However, it is also possible that through the valve 11.1 the high pressure of the refrigerant is regulated and the valve 4 the evaporator power at the outdoor heat exchanger 6 established.

Through the parallel connection of evaporator / outdoor heat exchanger 6 and evaporator / chiller 11 is an independent control of the two mass flows in the refrigerant pipes 3 and 30 possible. For example, the valve 4 the high pressure or the subcooling of the refrigerant and the valve 11.1 the power of the downstream evaporator / chiller 11 according to its power requirements, for example, by direct control of the water outlet temperature Tw at the heat exchanger 11b like this in 5a by an arrow between 11.1 and the exit point on the heat exchanger 11b is indicated. In this case, the regulation of the valve 11.1 be carried out in many areas regardless of the operating conditions of the refrigeration cycle.

This procedure can also be used in A / C operation with parallel-connected evaporators 8th and 11 (Battery cooling).

The advantage of this circuit after 4a This is because there is less dependence on packaging or construction at slightly lower COP, and that it is possible to regulate evaporator performance by the refrigerant.

In the circuit after 4b with series evaporators in operating mode 2 are the valves 10 and 14 closed, so at the distribution point 3.1 downstream of the condenser no distribution of the mass flow takes place. The heat exchanger 11a That chillers 11 is the total mass flow through the series connection with the outdoor heat exchanger 6 with the valve open 15 flows through, so that in 2 schematically reproduced series connection results.

Also in this circuit in 4b is the control valve 7 closed and the evaporator 8th out of order.

It should be noted that even with this circuit after 4b the phase separator 5 with the branch line 3a for a two-stage compaction can be omitted.

The control or expansion valve 4 regulates the high pressure or the subcooling of the refrigerant after the condenser / condenser 2 and the control or expansion valve 11.1 is fully open, so it has no function on the refrigerant. Through the valve 11.1 would be an influence on the evaporator performance at the chiller 11 only possible to a very limited extent.

The accumulator 9 puts in the circuit the 5b the exit state (constant steam content) after the evaporator / chiller 11 one.

Through the series connection of evaporator / outdoor heat exchanger 6 and evaporator / chiller 11 in 4b results in an equal refrigerant mass flow through both evaporators 6 and 11 , Wherein no or only a limited refrigerant side regulation of the performance of the individual evaporator is possible.

The advantage of the circuit in 4b This is because good COP can be achieved if compact packaging is possible, ie the line between outdoor heat exchangers 6 and the valves 10 . 14 and 11.1 can be short and formed with a large cross-section.

If the refrigerant circuit after 4a or 4b working in heat pump mode, can by the chiller 11 the waste heat z. B. the battery of an electric vehicle to increase the efficiency can be exploited.

In the circuit after 4c (A / C or cooling mode with parallel evaporators 8th and 11 according to operating mode 3 ) are the valves 10 and 14 closed and the control valve 4 is fully open, so it has no function. In the same way is the phase separator 5 without function. The line at 3a is shown interrupted to indicate the elimination of a two-stage compression.

The control or expansion valve 7 regulates the high pressure of the refrigerant or the subcooling to the outdoor heat exchanger / condenser 6 and thus the entry state in the two evaporators 8th and 11 ,

The accumulator 9 sets the exit state (constant steam content) both after the evaporator 8th as well as after the chiller 11 one.

It is thus the inlet and outlet state of the refrigerant to the evaporators 8th and 11 defined and the control valve 11.1 is no longer needed for controlling the inlet and outlet conditions of the evaporator.

In this cooling operation of the refrigerant circuit after 4c when connected in parallel evaporators 8th and 11 is an independent control of the two mass flows possible. For example, the valve 4 the high pressure or the subcooling of the refrigerant and the valve 11.1 the performance of the evaporator / chiller 11 according to its power requirements, whereby the water outlet temperature Tw can be controlled directly, as indicated by an arrow on the chiller 11 in 4c is indicated.

But it is also possible that by means of the valve 11.1 the high pressure of the refrigerant is regulated and by means of the valve 7 the evaporator power at the evaporator 8th is set.

The advantage of the circuit after 4c This is because even in cooling mode (A / C mode), an independent refrigerant-side capacity control of the chiller 11 is possible. This can z. B. the temperature of a water-cooled battery of an electric vehicle are accurately controlled, the cooling circuit to the evaporator / chiller 11 is connected, as already in the operating mode 1 was explained.

5 shows a further embodiment of the invention, wherein the refrigerant circuit is not a capacitor 2 like in the 1 to 4 and at the provided in a motor vehicle position of the outdoor heat exchanger 6 of the 1 to 4 a heat exchanger 60 is arranged, which works as a condenser.

The expansion or control valve 7 regulates the high pressure or the subcooling after the condenser 60 and thus the entry state in the two parallel evaporators 8th and 11 , The accumulator 9 sets the exit state (constant steam content) after the two evaporators 8th and 11 one. After the inlet and outlet state at the evaporators 8th and 11 through the control valve 7 and the accumulator 9 is defined, the expansion or control valve 11.1 no longer needed for the regulation of the refrigerant circuit.

In this refrigerant circuit independent control of the two mass flows is possible, with z. B. the one valve 7 the high pressure (or subcooling) regulates and the other valve 11.1 the power of the downstream second evaporator or chiller 11 according to its power requirements, in which z. B. the water outlet temperature Tw of the cooling water circuit of a battery is controlled directly.

It is also possible by means of the valve 11.1 to regulate the high pressure and by means of the valve 7 the evaporator capacity at the first evaporator 8th adjust.

The refrigerant circuit after 5 with parallel evaporators 8th and 11 is intended for cooling operation (A / C), whereby also in A / C operation an independent refrigerant-side capacity control of the chiller 11 is possible to z. B. to be able to control the temperature of a water-cooled battery exactly.

The setting of one of the two valves 7 and 11.1 Regardless of the conditions of the refrigerant circuit is in heat pump operation in 4a , in A / C operation of the heat pump in 4c and also in the cooling mode of a pure A / C system 5 possible, as indicated by an arrow at Tw in these figures.

QUOTES INCLUDE IN THE DESCRIPTION

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Cited patent literature

• DE 69629881 T2 [0002]

Claims (14)

Refrigerant circuit comprising a compressor ( 1 ), a capacitor ( 2 ), an outdoor heat exchanger ( 6 ) and a first evaporator ( 8th ), from which the refrigerant to the compressor ( 1 ), one through a valve ( 10 ) lockable and releasable bypass line ( 3b ) is provided, the first evaporator ( 8th ) bypasses and the outdoor heat exchanger ( 6 ) with the compressor ( 1 ), characterized in that in the refrigerant circuit, a second evaporator ( 11 ), which is the first evaporator ( 8th ) is connected in parallel. Refrigerant circuit according to claim 1, wherein the capacitor ( 2 ) a phase separator ( 5 ), the vaporous and liquid refrigerant separates, wherein the vapor refrigerant in the medium-pressure region the compressor ( 1 ) and the liquid refrigerant to the outdoor heat exchanger ( 6 ) is supplied. Refrigerant circuit according to claim 1 or 2, wherein the second evaporator ( 11 ) the outdoor heat exchanger ( 6 ) is connected in series. Refrigerant circuit according to claim 1 or 2, wherein the second evaporator ( 11 ) to the outdoor heat exchanger ( 6 ) is connected in parallel. Refrigerant circuit according to claim 3 or 4, wherein the control of at least one valve ( 15 ) can be switched between series connection and parallel connection. Refrigerant circuit according to claim 4 or 5, wherein the refrigerant line downstream of the capacitor ( 2 ) into a primary circuit ( 3 ) with the outdoor heat exchanger ( 6 ) as well as in a secondary circuit ( 30 ) with the second evaporator ( 11 ) divides and the two circles between outdoor heat exchanger ( 6 ) and second evaporator ( 11 ) are brought together again. Refrigerant circuit according to claim 6, wherein of the refrigerant line ( 3 ) after the capacitor ( 2 ) a branch line ( 30 ) branches off with the refrigerant line ( 3 ) before the second evaporator ( 11 ) and in which a valve ( 14 ) is arranged to shut off and release. Refrigerant circuit according to claim 3, wherein in series connection, the connection path between the outdoor heat exchanger ( 6 ) and second evaporator ( 11 ) is designed so that the associated line volume is as small as possible. Refrigerant circuit according to claim 8, wherein the associated line internal volume less than 30%, preferably less than 10% of the usable storage volume of an accumulator ( 9 ). Refrigerant circuit according to one of claims 4 to 6, wherein the connection path between the outdoor heat exchanger ( 6 ) and branch to the second evaporator ( 11 ) has a considerably larger cross section than between the branch to the second evaporator ( 11 ) and the first evaporator ( 8th ). Refrigerant circuit according to claim 10, wherein the connection path between the outdoor heat exchanger ( 6 ) and branch to the second evaporator ( 11 ) is considerably shorter than between the branch to the second evaporator ( 11 ) and the first evaporator ( 8th ). Refrigerant circuit according to one of the preceding claims, wherein each of the parallel-connected evaporator ( 8th . 11 ) each an expansion or control valve ( 7 . 11.1 ) and the two evaporators ( 8th . 11 ) an accumulator ( 9 ) and one of the valves ( 7 or 11.1 ) is adjustable independently of the conditions of the refrigerant circuit. Refrigerant circuit comprising a compressor ( 1 ), a liquefier ( 60 ) and at least two evaporators connected in parallel ( 8th . 11 ), which in each case by a separate valve ( 7 and 11.1 ), wherein at least one of the valves ( 7 . 11.1 ) is adjustable independently of parameters to be controlled of the refrigerant circuit and the two evaporators an accumulator ( 4 ) is connected downstream. Refrigerant circuit according to one of the preceding claims, wherein the second evaporator ( 11 ) is in heat exchange with a vehicle component, such as a battery, an inverter, an electric motor or the like.

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