DE102016004999B3 - Vehicle air conditioning - Google Patents

Abstract

The invention relates to a vehicle air conditioner (1) having a refrigerant circuit (2) which can be operated as a heat pump cycle with a cooling function and which has an evaporator (3), a refrigerant compressor (4), a refrigerant condenser / gas cooler (5.1), an evaporator ( 3) associated first expansion element (6.1), a refrigerant compressor (4) downstream high-pressure refrigerant-refrigerant heat exchanger (7) and a thermally thermally coupled to the high-pressure refrigerant refrigerant heat exchanger (7) heat exchanger (7.1) for carrying out the Includes heating function. According to the invention, a second expansion element (6.2) and a downstream in the flow direction of the refrigerant circuit (2) check valve (R1) are provided as the first heat pump branch (WPZ1) to realize the heating function, the reversal of the flow direction in the first heat pump branch (WPZ1) the check valve (R1) is prevented, and by means of a valve arrangement (V, V1, V2, V3) the first heat pump branch (WPZ1) for forming a first heat pump cycle with the refrigerant compressor (4) and the high-pressure refrigerant refrigerant heat exchanger (7) under the arrangement of the second expansion element (6.2) in the flow direction of the refrigerant circuit (2) is fluidly connected downstream of the high-pressure refrigerant-refrigerant heat exchanger (7), wherein by means of the first heat pump cycle process a recovery of the heat absorbed by the refrigerant waste heat of the refrigerant compressor (4) is effected ,

Description

The invention relates to a vehicle air conditioning system with a heat pump cycle with a heating function and as a refrigeration cycle with cooling function operable refrigerant circuit. Furthermore, the invention relates to a vehicle with a vehicle air conditioning system according to the invention.

It is known that vehicles, in particular also electric vehicles, are equipped with an air conditioning system which can be switched from a cold operation to a heat operation or cooling and heating operation and vice versa.

Furthermore, vehicle air conditioning systems are known whose refrigerant circuit has a designed as a high-pressure refrigerant-refrigerant heat exchanger indirect capacitor, which has a heat pump on a condenser side coolant circuit as a heat sink and heated there via the integrated downstream heating heat exchanger, the supply air of the vehicle interior. In addition to at least one interior evaporator, electrified vehicles require a separate coolant circuit for conditioning and temperature control of the energy accumulator, which is generally realized as a high-voltage battery. Such a coolant circuit can be coupled by means of a heat exchanger with the refrigerant circuit, wherein such a heat exchanger in turn is also designed as an evaporator for cooling an air flow or as a so-called chiller for cooling water. Alternatively, the cooling of an energy store or other high-voltage components can also take place via direct evaporation of refrigerant in the component.

Also, the use of the refrigerant circuit of a vehicle air conditioner in a heat pump operation for heating the passenger compartment is known. In its interconnection or function as a heat pump, the refrigerant circuit is able to heat an air or water flow or coolant flow and deliver this heat directly or indirectly to the supply air of the passenger compartment.

A vehicle air conditioning system with an evaporator, a refrigerant compressor, a refrigerant condenser, a first expansion element associated with the evaporator and a refrigerant-refrigerant heat exchanger is known from US Pat DE 10 2010 051 976 A1 known. In heating operation, a supply air flowing into the vehicle interior is heated by means of a heating heat exchanger, this heating heat exchanger being thermally coupled via a coolant circuit to a drive unit, for example a drive unit. In heat pump operation, the refrigerant compressed by the refrigerant compressor is guided via the high-pressure refrigerant-refrigerant heat exchanger, where part of the heat of the refrigerant is transferred to the refrigerant circuit for heating the passenger compartment. This high-pressure refrigerant coolant heat exchanger downstream of another refrigerant condenser is connected as a heating coil in the flow direction, which emits heat directly to the air flowing into the vehicle interior supply air in heating and preheats this directly as it flows into the air conditioner. Thus, this serving as a preheater heater is arranged at the air inlet to the air conditioner and upstream of the evaporator in the flow direction of the supply air. This serving as a heater further refrigerant condenser is thus designed as a direct heat exchanger and integrated into the supply air flow for the occupant cabin.

Known heat pump systems with carbon dioxide (R744) as a refrigerant, as for example. In the DE 101 63 607 A1 be described, use for heating the cabin air maximum of two heat sources in the vehicle. Each additional heat source makes the system design more complex and requires additional control and regulation to ensure proper operation.

In particular, in the case of pure electric vehicles, the question arises as to how most effective and efficient cabin heating can be realized, with such pure electric vehicles instead of a mechanical refrigerant compressor generally having refrigeration circuits fitted with electrical refrigerant compressors. If electric heaters are used on high or low voltage basis, this leads to a high energy requirement, which has a considerable influence on the range of the electric vehicle.

The DE 10 2012 208 992 A1 proposes a heating and cooling circuit that covers all major operating programs such as heating, cooling, mixed operation and de-icing of Außenwärmeübertragers in an electric vehicle. For this purpose, this heating and cooling circuit comprises a refrigerant compressor, which has an input for a medium-pressure injection in addition to a low pressure input. Furthermore, this heating and cooling circuit comprises at least one Hochdruckexpansionsorgan, is relaxed with the refrigerant from a high pressure level to the intermediate pressure level, wherein a medium-pressure heat exchanger is provided for the evaporator provided in the air conditioner of the vehicle. An outlet for liquid refrigerant having separator of this known heating and cooling circuit is supplied to the effluent from the medium-pressure heat exchanger refrigerant, via a gas outlet of the separator gaseous refrigerant can flow to the medium pressure input of the refrigerant compressor. Finally, in this known heating and cooling circuit a Mitteldruckexpansionsorgan switched over which is released from the liquid refrigerant outlet of the separator coming liquid refrigerant to a low pressure level. After relaxation to the low pressure level, the refrigerant flows through a low-pressure external heat exchanger.

It is an object of the invention to provide a vehicle air conditioning system with which an efficient and efficient cabin heating is made possible in electric vehicles.

This object is achieved by a vehicle air conditioning system with the features of patent claim 1 and with the features of patent claim 2.

• – einen Verdampfer, einen Kältemittelverdichter, einen Kältemittelkondensator/Gaskühler, ein dem Verdampfer zugeordnetes erstes Expansionsorgan,
• – einen dem Kältemittelverdichter nachgeschalteten Hochdruck-Kältemittel-Kühlmittel-Wärmeübertrager, und
• – einen thermisch mit dem Hochdruck-Kältemittel-Kühlmittel-Wärmeübertrager thermisch gekoppelten Heizungswärmeübertrager zur Durchführung der Heizfunktion, wobei – zur Realisierung der Heizfunktion ein zweites Expansionsorgan und ein in Strömungsrichtung des Kältemittelkreislaufs nachgeschaltetes Rückschlagventil als erster Wärmepumpenzweig vorgesehen sind, wobei die Umkehrung der Strömungsrichtung im ersten Wärmepumpenzweig durch das Rückschlagventil verhindert ist,
• – mittels einer Ventilanordnung der erste Wärmepumpenzweig zur Bildung eines ersten Wärmepumpenkreisprozesses mit dem Kältemittelverdichter und dem Hochdruck-Kältemittel-Kühlmittel-Wärmeübertrager unter Anordnung des zweiten Expansionsorgans in Strömungsrichtung des Kältemittelkreislaufs stromabwärts nach dem Hochdruck-Kältemittel-Kühlmittel-Wärmeübertrager fluidverbunden ist, wobei mittels des ersten Wärmepumpenkreisprozesses eine Rückgewinnung der vom Kühlmittel aufgenommenen Abwärme des Kältemittelverdichters bewirkt ist, und
• – die Ventilanordnung dem Hochdruck-Kältemittel-Kühlmittel-Wärmeübertrager in Strömungsrichtung des Kältemittelkreislaufs nachgeschaltet ist, wobei mittels der Ventilanordnung das Kältemittel im Kältebetrieb über den Kältemittelkondensator/Gaskühler und zur Realisierung der Heizfunktion mittels des Wärmepumpenkreisprozesses über den ersten Wärmepumpenzweig geführt ist.

A vehicle air conditioning system with a refrigerant circuit which can be operated as a heat pump cycle with a heating function and as a refrigeration cycle with a cooling function comprises according to the first-mentioned solution:

• An evaporator, a refrigerant compressor, a refrigerant condenser / gas cooler, a first expansion element associated with the evaporator,
• - A refrigerant compressor downstream high-pressure refrigerant refrigerant heat exchanger, and
• - A thermally coupled to the high-pressure refrigerant-refrigerant heat exchanger heat exchanger for performing the heating function, - are provided for the realization of the heating function, a second expansion element and downstream in the flow direction of the refrigerant circuit check valve as the first heat pump branch, the reversal of the flow direction in the first Heat pump branch is prevented by the check valve,
• - By means of a valve arrangement of the first heat pump branch for forming a first heat pump cycle with the refrigerant compressor and the high-pressure refrigerant refrigerant heat exchanger under arrangement of the second expansion element in the flow direction of the refrigerant circuit downstream of the high-pressure refrigerant refrigerant heat exchanger fluidly connected, wherein by means of the first Heat pump cycle process, a recovery of the refrigerant absorbed waste heat of the refrigerant compressor is effected, and
• - The valve assembly is connected downstream of the high-pressure refrigerant-refrigerant heat exchanger in the flow direction of the refrigerant circuit, wherein by means of the valve arrangement, the refrigerant is performed in the cooling mode via the refrigerant condenser / gas cooler and to realize the heating function by means of the heat pump cycle over the first heat pump branch.

With this vehicle air conditioning system according to the invention, the refrigerant compressor is also used as a heat source by the waste heat, in particular in the case of a used in electric vehicles electric refrigerant compressor is transmitted to the thermally coupled with the high-pressure refrigerant refrigerant heat exchanger heat exchanger, which in direct exchange with the air Vehicle interior, for example. An electric vehicle is. For such a vehicle air conditioning system only a small demand for components is required. The check valve prevents refrigerant from entering the first heat pump branch in air conditioning mode (AC mode). The refrigerant-refrigerant heat exchanger operates as a high-pressure heat exchanger and is also referred to as an indirect condenser or gas cooler.

The valve arrangement is connected downstream of the high-pressure refrigerant-coolant heat exchanger in the flow direction of the refrigerant circuit, wherein the refrigerant is conducted by the valve arrangement in the cooling mode via the refrigerant condenser / gas cooler and to realize the heating function by means of the first heat pump cycle over the first heat pump branch.

• – einen Verdampfer, einen Kältemittelverdichter, einen Kältemittelkondensator/Gaskühler, ein dem Verdampfer zugeordnetes erstes Expansionsorgan,
• – einen dem Kältemittelverdichter nachgeschalteten Hochdruck-Kältemittel-Kühlmittel-Wärmeübertrager, und
• – einen thermisch mit dem Hochdruck-Kältemittel-Kühlmittel-Wärmeübertrager thermisch gekoppelten Heizungswärmeübertrager zur Durchführung der Heizfunktion, wobei – zur Realisierung der Heizfunktion ein zweites Expansionsorgan und ein in Strömungsrichtung des Kältemittelkreislaufs nachgeschaltetes Rückschlagventil als erster Wärmepumpenzweig vorgesehen sind, wobei die Umkehrung der Strömungsrichtung im ersten Wärmepumpenzweig durch das Rückschlagventil verhindert ist,
• – mittels einer Ventilanordnung der erste Wärmepumpenzweig zur Bildung eines ersten Wärmepumpenkreisprozesses mit dem Kältemittelverdichter und dem Hochdruck-Kältemittel-Kühlmittel-Wärmeübertrager unter Anordnung des zweiten Expansionsorgans in Strömungsrichtung des Kältemittelkreislaufs stromabwärts nach dem Hochdruck-Kältemittel-Kühlmittel-Wärmeübertrager fluidverbunden ist, wobei mittels des ersten Wärmepumpenkreisprozesses eine Rückgewinnung der vom Kühlmittel aufgenommenen Abwärme des Kältemittelverdichters bewirkt ist, und
• – die Ventilanordnung dem Kältemittelverdichter in Strömungsrichtung des Kältemittelkreislaufs nachgeschaltet ist, wobei mittels der Ventilanordnung das Kältemittel im Kältebetrieb über den Kältemittelkondensator/Gaskühler und zur Realisierung der Heizfunktion mittels des ersten Wärmepumpenkreisprozesses über den Kältemittel-Kühlmittel-Wärmeübertrager und anschließend den ersten Wärmepumpenzweig geführt ist. Bei dieser Ausführung wird der Kältemittel-Kühlmittel-Wärmeübertrager nur im Heizbetrieb von Kältemittel durchströmt, jedoch nicht während eines Kühlbetriebes der Fahrzeugklimaanlage.

A vehicle air conditioning system with a refrigerant circuit which can be operated as a heat pump cycle with a heating function and as a refrigeration cycle with a cooling function comprises, according to the second-mentioned solution:

• An evaporator, a refrigerant compressor, a refrigerant condenser / gas cooler, a first expansion element associated with the evaporator,
• - A refrigerant compressor downstream high-pressure refrigerant refrigerant heat exchanger, and
• - A thermally coupled to the high-pressure refrigerant-refrigerant heat exchanger heat exchanger for performing the heating function, - are provided for the realization of the heating function, a second expansion element and downstream in the flow direction of the refrigerant circuit check valve as the first heat pump branch, the reversal of the flow direction in the first Heat pump branch is prevented by the check valve,
• By means of a valve arrangement, the first heat pump branch to form a first heat pump circuit process with the refrigerant compressor and the high-pressure Refrigerant-refrigerant heat exchanger is fluidly connected under arrangement of the second expansion member in the flow direction of the refrigerant circuit downstream of the high-pressure refrigerant refrigerant heat exchanger, wherein by means of the first heat pump cycle process, a recovery of the refrigerant absorbed waste heat of the refrigerant compressor is effected, and
• - The valve assembly is connected downstream of the refrigerant compressor in the flow direction of the refrigerant circuit, wherein by means of the valve arrangement, the refrigerant in the refrigeration operation via the refrigerant condenser / gas cooler and to realize the heating function by means of the first heat pump cycle via the refrigerant-refrigerant heat exchanger and then the first heat pump branch is performed. In this embodiment, the refrigerant-refrigerant heat exchanger is flowed through only in the heating mode of refrigerant, but not during a cooling operation of the vehicle air conditioner.

A further embodiment of the invention provides that in the flow direction of the refrigerant circuit, a heating coil is arranged downstream of the refrigerant-refrigerant heat exchanger. Thus, a 2-stage cooling of the refrigerant is first realized at the same pressure level, namely at high pressure level, this heater is arranged as a direct heat exchanger in an air conditioner of the vehicle air conditioning. This heater as well as the heating heat exchanger can be installed in a compact arrangement in the air conditioner, in which situation the heater is positioned on the air side in the air conditioner between the evaporator and the heater core. In order to provide this space, the heating heat exchanger is offset in the direction of the air flow and thus made available the space for accommodating the heating register.

A particularly advantageous development of the invention results when the heating coil is integrated into the first heat pump cycle. For this purpose, it is provided that the heating coil is connected in the flow direction of the refrigerant circuit upstream with the second expansion element of the first heat pump branch. As a result, the coolant is flowed through by the refrigerant-coolant heat exchanger downstream, first the heating register, then the second expansion element and finally the check valve of the first heat pump branch.

According to a further embodiment of the invention, the first heat pump branch upstream of an inner heat exchanger is arranged in the flow direction of the refrigerant circuit, which is fluidly connected to the refrigerant compressor. Further, preferably in the flow direction of the refrigerant circuit, the first heat pump branch upstream of a refrigerant collector arranged upstream of the inner heat exchanger. In this way, it is ensured that the system is always actively supplied with refrigerant from the refrigerant collector when needed and in the other case can store refrigerant in it.

• – zur Realisierung der Heizfunktion ein zweiter Wärmepumpenzweig mittels des Kältemittelkondensators/Gaskühlers, einem in Strömungsrichtung des Kältemittelkreislaufs stromaufwärts vor dem Kältemittelkondensator/Gaskühler angeordneten dritten Expansionsorgan und einem in Strömungsrichtung des Kältemittelkreislaufs stromaufwärts vor dem dritten Expansionsorgan angeordneten Rückschlagventil vorgesehen ist, wobei die Umkehrung der Strömungsrichtung im zweiten Wärmepumpenzweig durch das Rückschlagventil verhindert ist, und
• – mittels einer Ventilanordnung der zweite Wärmepumpenzweig zur Bildung eines zweiten Wärmepumpenkreisprozesses einerseits in Strömungsrichtung des Kältemittelkreislaufs dem ersten Wärmepumpenzweig oder dem Rückschlagventil des ersten Wärmepumpenzweiges vorgeschaltet ist und andererseits mit dem Kältemittelverdichter und dem Kältemittel-Kühlmittel-Wärmeübertrager unter Anordnung des Rückschlagventils in Strömungsrichtung des Kältemittelkreislaufs stromabwärts nach dem Kältemittel-Kühlmittel-Wärmeübertrager fluidverbunden ist, wobei mittels des zweiten Wärmepumpenkreisprozesses eine Rückgewinnung der vom Kältemittel mittels des Kältemittelkondensators/Gaskühlers aufgenommene Umgebungswärme bewirkt ist.

A particularly advantageous embodiment of the invention provides that

• - Provided for the realization of the heating function, a second heat pump branch by means of the refrigerant condenser / gas cooler, upstream of the refrigerant condenser / gas cooler arranged in the flow direction of the refrigerant circuit third expansion element and upstream in the flow direction of the refrigerant circuit upstream of the third expansion valve check valve, wherein the inversion of the flow direction in second heat pump branch is prevented by the check valve, and
• - By means of a valve arrangement of the second heat pump branch to form a second heat pump cycle on the one hand in the flow direction of the refrigerant circuit the first heat pump branch or the check valve of the first heat pump branch upstream and on the other hand with the refrigerant compressor and the refrigerant-refrigerant heat exchanger with arrangement of the check valve in the flow direction of the refrigerant circuit downstream the refrigerant-refrigerant heat exchanger fluidly connected, wherein by means of the second heat pump cycle process, a recovery of the refrigerant absorbed by means of the refrigerant condenser / gas cooler ambient heat is effected.

In this embodiment of the invention, heat from the surroundings of the vehicle is received as a further heat source by means of the refrigerant condenser / gas cooler and used for heating the supply air flow of the vehicle interior. In this case, not only the heat from the ambient air, but also from the engine room circulating air can be used. It is particularly advantageous if the inner heat exchanger is arranged between the check valve of the second heat pump branch and the third expansion element. With the check valve is in AC mode filling, u. a. the heating register and a relocating the refrigerant in this prevented. Preferably, in this embodiment of the invention, the inner heat exchanger is connected between the check valve of the second heat pump branch and the third expansion element.

• – zur Realisierung der Heizfunktion ein viertes Expansionsorgan und ein in Strömungsrichtung des Kältemittelkreislaufs nachgeschalteter Niederdruck-Kältemittel-Kühlmittel-Wärmeübertrager, dem sogenannten Chiller, als dritter Wärmepumpenzweig vorgesehen sind, und
• – mittels einer Ventilanordnung der dritte Wärmepumpenzweig zur Bildung eines dritten Wärmepumpenkreisprozesses mit dem Kältemittelverdichter und dem Hochdruck-Kältemittel-Kühlmittel-Wärmeübertrager, dem sogenannten indirekten Kältemittelkondensator oder Gaskühler unter Anordnung des vierten Expansionsorgans in Strömungsrichtung des Kältemittelkreislaufs stromabwärts nach dem Hochdruck-Kältemittel-Kühlmittel-Wärmeübertrager fluidverbunden ist, wobei mittels des dritten Wärmepumpenkreisprozesses eine Rückgewinnung der vom Kühlmittel mittels des Niederdruck-Kältemittel-Kühlmittel-Wärmeübertragers aufgenommenen Abwärme von elektrischen Komponenten bewirkt ist.

Another particularly advantageous embodiment of the invention provides that

• - For the realization of the heating function, a fourth expansion element and downstream in the flow direction of the refrigerant circuit low-pressure refrigerant refrigerant heat exchanger, the so-called chiller, are provided as the third heat pump branch, and
• By means of a valve arrangement, the third heat pump branch to form a third heat pump cycle with the refrigerant compressor and the high-pressure refrigerant refrigerant heat exchanger, the so-called indirect refrigerant condenser or gas cooler with arrangement of the fourth expansion element in the flow direction of the refrigerant circuit downstream of the high-pressure refrigerant-refrigerant heat exchanger is fluid-connected, wherein by means of the third heat pump cycle process, a recovery of the heat absorbed by the refrigerant by means of the low-pressure refrigerant-refrigerant heat exchanger waste heat of electrical components is effected.

In this embodiment of the invention, by means of operating at low pressure level low-pressure refrigerant-refrigerant heat exchanger, the so-called chiller, the waste heat from electrical components of the vehicle recorded as a further heat source of the vehicle and used to heat the vehicle interior.

According to a further embodiment of the invention, it is advantageous if the high-pressure refrigerant-refrigerant heat exchanger operating at high pressure level is followed by a fifth expansion element. Thus, the fifth expansion element downstream heater can be performed as a low-pressure component with reduced strength requirements.

Finally, according to a further advantageous embodiment of the invention, the high-pressure refrigerant-refrigerant heat exchanger and the heating coil are functionally combined in one component. Thus, the heat bound in the refrigerant is transferred to the cabin air flow via direct gas cooling or condensation, wherein the heater has an increasing block depth and the heater core, however, can be performed with a reduced block depth.

The vehicle air conditioning system according to the invention can be used in all types of vehicles. As a refrigerant for this vehicle air conditioner according to the invention not only R744, but also all other refrigerants can be used.

The invention will now be described in detail by means of embodiments with reference to the accompanying figures. Show it:

1 1 is a circuit diagram of a vehicle air conditioning system having first, second and third heat pump functions according to the invention;

2 a circuit diagram of the vehicle air conditioning after 1 in an alternative embodiment,

3 a circuit diagram of the vehicle air conditioning after 1 in a further alternative embodiment,

4 3 is a circuit diagram of another vehicle air conditioning system having first, second and third heat pump functions according to the invention;

5 a circuit diagram of the vehicle air conditioning after 4 in an alternative embodiment,

6 a circuit diagram of the vehicle air conditioning after 4 in a further alternative embodiment.

The in the 1 to 6 illustrated vehicle air conditioning systems according to the invention 1 have refrigerant circuits 2 which agree in their basic structure. First, this basic structure of the refrigerant circuits 2 for this 1 to 6 explained and then the embodiments are described according to the individual figures with their differences.

For the sake of simplicity, in the 1 to 6 in the system presentation on the presentation and introduction of other known to the skilled person functionally required components, such as suction lines dead volumes, that is dispensed depending on the respective selected system interconnection inactive system sections. The same applies to the positioning of check valves at the outlet of a gas cooler or a heater or a capacitor to prevent refrigerant backflow into the respective inactive sector of the system, unless it is for the explanation of the operation of the vehicle air conditioner 1 required are.

Every refrigerant circuit 2 according to the 1 to 6 consists of an evaporator 3 , a refrigerant compressor 4 , a refrigerant condenser or gas cooler 5.1 , a heating register 5.2 as a further refrigerant condenser or gas cooler, designed as an expansion valve first expansion element 6.1 which is the evaporator 3 upstream, an internal heat exchanger 8th and a refrigerant collector 9 using as refrigerant carbon dioxide (R744).

In the flow direction of the refrigerant circuit 2 is the refrigerant compressor 4 downstream of a high pressure refrigerant high pressure refrigerant heat exchanger 7 downstream, via a heating circuit 11 thermally with a designed as a coolant-air heat exchanger heater heat exchanger 7.1 is thermally coupled with water as a coolant. With a water pump 12 the fluid is in the heating circuit 11 circulated.

The evaporator 3 , the heater heat exchanger 7.1 and the heating register 5.2 are in accordance with the 1 to 6 together in an air conditioner 1.1 the vehicle air conditioner 1 accommodated.

In heat pump operation of the refrigerant circuit 2 is in the embodiments according to the 1 to 6 by means of the high-pressure high-pressure refrigerant-refrigerant heat exchanger 7 the refrigerant cooled and thus transferred to the water as coolant heat the heater core 7.1 supplied, with which the vehicle interior supplied air is heated directly.

A further refrigerant cooling takes place in the embodiments according to the 1 to 5 by means of the high-pressure refrigerant-refrigerant heat exchanger 7 in the flow direction of the refrigerant downstream heater 5.2 inside the air conditioner 1.1 , Thus, the cooling of the refrigerant flow is carried out in two stages, wherein the air to be conditioned in the vehicle interior on the one hand by means of the heating circuit 11 indirectly and by means of the heating register 5.2 is heated directly. The situation is similar in the exemplary embodiment 6 except that here on a separate high-pressure refrigerant-refrigerant heat exchanger 7 dispensed with and its function in a single and larger sized heater 5.3 is transferred. The refrigerant thus flows from the refrigerant compressor 4 directly to a heating register 5.3 , The heating heat exchanger 7.2 can be done with a smaller size (block depth).

To carry out the heat pump operation several heat sources are used in the vehicle.

A first heat pump cycle process uses the refrigerant compressor as a heat source 4 whose waste heat is used in the form of the drive power of the refrigerant compressor for heating the air supplied to the vehicle interior. Such waste heat is generated in particular in electric refrigerant compressors, which are used in pure electric vehicles.

For this purpose, the refrigerant circuit 2 according to the 1 to 6 a first heat pump branch WPZ1, which consists of a in the flow direction of the refrigerant circuit 2 arranged, designed as an expansion valve second expansion element 6.2 and a downstream of this downstream check valve R1. This check valve R1 prevents a flow reversal from the check valve R1 back into the second expansion element 6.2 to prevent the inflow of refrigerant into the heating coil 5.2 to avoid in AC mode. This first heat pump branch WPZ1 forms together with the series circuit of refrigerant compressor 4 and this downstream high-pressure refrigerant-refrigerant heat exchanger 7 the first heat pump cycle in which in the flow direction of the refrigerant circuit 2 the second expansion valve 6.2 downstream of the high pressure refrigerant refrigerant heat exchanger 7 is connected downstream by means of a valve arrangement V. In detail, this first heat pump cycle process will be described in conjunction with the description of the respective ones 1 to 4 described.

A second heat pump cycle uses as a heat source the ambient air of the vehicle, the heat of which is used to heat the air supplied to the vehicle interior.

For this purpose, the refrigerant circuit 2 according to the 1 to 6 a second heat pump branch WPZ2 from the refrigerant condenser / gas cooler 5.1 , one in the flow direction of the refrigerant circuit 2 upstream of the refrigerant condenser / gas cooler 5.1 arranged, designed as an expansion valve third expansion element 6.3 and one in the flow direction of the refrigerant circuit 2 upstream of the third expansion element 6.3 arranged check valve R2 is formed, wherein the reversal of the flow direction of the refrigerant from the refrigerant condenser / gas cooler 5.1 back to the heater 5.2 respectively. 5.3 is prevented by the check valve R2. This second heat pump branch WPZ2 forms together with the series circuit of refrigerant compressor 4 and this downstream high-pressure refrigerant-refrigerant heat exchanger 7 the second heat pump cycle, in which the second heat pump branch WPZ2 by means of a valve arrangement V on the one hand in the flow direction of the refrigerant circuit 2 the first heat pump branch WPZ1 (see. 1 to 3 ) or the check valve R1 of the first heat pump branch WPZ1 (cf. 4 to 6 ) upstream and on the other hand with the refrigerant compressor 4 and the high-pressure refrigerant-refrigerant heat exchanger 7 under the arrangement of the check valve R2 in the flow direction of the refrigerant circuit 2 downstream of the high pressure refrigerant refrigerant heat exchanger 7 fluidly connected. In detail, this second heat pump cycle process will be described in conjunction with the description of the respective ones 1 to 6 described.

A third heat pump cycle process uses as heat source the waste heat of electrical components, such as high voltage batteries, electric motors or power electronics.

For this purpose, the refrigerant circuit 2 according to the 1 to 6 a third heat pump branch WPZ3, which consists of a designed as an expansion valve fourth expansion element 6.4 and one in the flow direction of the refrigerant circuit 2 downstream, working at low pressure level low-pressure refrigerant-refrigerant heat exchanger 10 , called chiller in the following, consists. This third heat pump branch WPZ3 together with the series circuit of refrigerant compressor 4 and this downstream high-pressure refrigerant-refrigerant heat exchanger 7 the third heat pump cycle, in which the fourth expansion element 6.4 in the flow direction of the refrigerant circuit 2 downstream of the high pressure refrigerant refrigerant heat exchanger 7 is connected downstream by means of a valve arrangement V. In detail, this third heat pump cycle process will be described in conjunction with the description of the respective ones 1 to 6 described.

This chiller 10 forms according to the 1 to 6 together with a heat source 13 a coolant circuit 14 and serves to remove that from the heat source 13 on the coolant of the coolant circuit 14 absorbed heat to the refrigerant circuit 2 , so to transfer to the refrigerant, in this capacity the chiller 10 together with the fourth expansion organ 6.4 works as an evaporator. With this heat is then, as already mentioned above, on the one hand by means of the high-pressure refrigerant-coolant heat exchanger 7 the air supplied to the vehicle interior indirectly and by means of the heating register 5.2 heated directly.

As an alternative possibility for the realization of the first heat pump circuit process, it makes sense that the chiller 10 associated fourth expansion organ 6.4 instead of the second expansion organ 6.2 of the first heat pump branch WPZ1. For this purpose, the water-side flow through the chiller 10 stopped, ie the coolant remains "standing" in the chiller 10 , so no heat transfer at the chiller 10 can take place. In this mode of operation, the refrigerant passes through the refrigerant compressor 4 , the high pressure refrigerant heat exchanger 7 , the heating register 5.2 and the internal heat exchanger 8th by means of the fourth expansion organ 6.4 in the chiller 10 relaxes and then flows through the check valve R3, the refrigerant collector 9 and the internal heat exchanger 8th back to the refrigerant compressor 4 ,

Furthermore, according to the 1 to 6 both the evaporator 3 as well as the chiller 10 each downstream of a check valve R3 and R4 downstream, so that a flow reversal of the refrigerant via these check valves R3 and R4 back into the evaporator 3 or the chiller 10 , Especially in the case of their non-active functional integration into the respective set operating mode of the refrigerant circuit 2 , is prevented. The check valves R3 and R4 and the check valve R1 of the first heat pump branch WPZ1 form together with the refrigerant collector 9 a node through which the refrigerant from the check valves R1, R3 and R4 in the refrigerant collector 9 flows.

Another commonality of the vehicle air conditioning 1 according to the 1 to 6 is that the two expansion organs 6.1 and 6.4 So the first expansion organ 6.1 and the fourth expansion organ 6.4 downstream via their associated evaporator 3 or chiller 10 with the inlet side of the refrigerant collector 9 fluidly connected.

According to the 1 . 2 and 3 can be the high-pressure refrigerant coolant heat exchanger 7 by means of the valve assembly V downstream either with the gas cooler 5.1 , the first heat pump branch WPZ1 or the heating coil 5.2 be fluidly connected, wherein the direct interconnection of the high-pressure refrigerant-refrigerant heat exchanger 7 with the condenser or gas cooler 5.1 only in AC mode. For this purpose, the high-pressure refrigerant coolant heat exchanger 7 either via a first shut-off valve V1 with the first heat pump branch WPZ1 or via a second shut-off valve V2 with the heating register 5.2 be fluidly connected. By means of a third shut-off valve V3, which the first shut-off valve V1 with the gas cooler 5.1 connects, the high pressure refrigerant coolant heat exchanger 7 downstream with the gas cooler 5.1 be fluidly connected, in which case the second expansion organ 6.2 of the first heat pump branch WPZ1 is provided with a shut-off function, so that the heat pump branch WPZ1 in the case of the cooling operation of the vehicle air conditioner 1 closed is.

To 1 the heating operation by means of the first heat pump cycle process using the first heat pump branch WPZ1, by means of the second heat pump cycle process using the second heat pump branch WPZ2 or by the third heat pump cycle process using the third heat pump branch WPZ3, wherein the first and third, and the second and third heat pump cycle process can be concurrent.

To carry out the first heat pump cycle process, the first shut-off valve V1 is opened, while the second shut-off valve V2 and the third shut-off valve V3 of the valve arrangement V are blocked, so that the refrigerant in the flow direction S of the refrigerant circuit 2 from the high-pressure refrigerant-refrigerant heat exchanger 7 flows into the first heat pump branch WPZ1, wherein by means of the second expansion element 6.2 the refrigerant is released at low pressure level. Via the check valve R1, the refrigerant flows through the refrigerant collector 9 and the internal heat exchanger 8th back to the refrigerant compressor 4 , The internal heat exchanger 8th However, in this heating mode by means of the first heat pump cycle process is not active.

To implement the second heat pump cycle process, the first shut-off valve V1 is closed and the second shut-off valve V2 is opened, whereby the coolant via the heating 5.2 into the second heat pump branch WPZ2 and then via the opened third shut-off valve V3 into the first heat pump branch WPZ1 and finally back again via the refrigerant collector 9 and the internal heat exchanger 8th in the refrigerant compressor 4 can flow. Also in this heating operation by means of the second heat pump cycle process is the internal heat exchanger 8th not active. It is important to ensure that the expansion organ 6.3 at maximum opening with its flow cross-sectional area close to the cross-section of the air conditioning lines upstream of the second expansion element 6.2 must be enough to almost exclude flow losses. It is also advantageous for the second heat pump branch WPZ2 if the line cross-sections are designed to the extent of the low-pressure-side air conditioning lines in order to largely eliminate said pressure losses.

During the heating process by means of the second heat pump cycle process, the refrigerant by means of the third expansion element 6.3 relaxed to low pressure, therefore, the wiring harness is out of the gas cooler 5.1 , the third shut-off valve V3, the second expansion element 6.2 and to dethrottle the check valve R1, that is possible to raise to a diameter of the low-pressure lines, to keep flow losses low.

Ideally, the shut-off valve V3 can be bidirectionally flowed through and the cross-sectional area can be raised or dimensioned to the extent of the low-pressure line mentioned.

To 1 is after the check valve R2 of the second heat pump branch WPZ2 in the flow direction S of the refrigerant circuit 2 a branch to the high pressure side of the inner heat exchanger 8th provided, making the second heat pump branch WPZ2 with the two expansion organs 6.1 and 6.4 fluidly connected. During the heating operation by means of the second heat pump cycle process, however, the refrigerant is prevented after the check valve R2 via the internal heat exchanger 8th in the evaporator 3 and the chiller 10 can flow as the two expansion organs 6.1 and 6.4 equipped with a shut-off function. Therefore, these two expansion organs 6.1 and 6.4 locked during the heating operation with the second heat pump cycle process.

For carrying out the third heat pump cycle process by means of the third heat pump branch WPZ3, the first shut-off valve V1 is closed and the second shut-off valve V2 is opened, whereby the refrigerant via the heating 5.2 , the check valve R2 of the second heat pump branch WPZ2 and the internal heat exchanger 8th in the chiller 10 by means of the fourth expansion organ 6.4 is relaxed, at the same time the first and third expansion organ 6.1 and 6.3 be locked because both expansion organs 6.1 and 6.3 each equipped with a shut-off function. This prevents both refrigerant by means of the first expansion element 6.1 in the evaporator 3 as well as refrigerant by means of the third expansion element 6.3 in the gas cooler 5.1 relaxed or relocated.

To carry out a cooling operation of the vehicle air conditioner 1 become the second shut-off valve V2 and the second expansion element 6.2 closed while the first shut-off valve V1 and the third shut-off valve V3 are opened, whereby the refrigerant from the high-pressure refrigerant-refrigerant heat exchanger 7 over the gas cooler 5.1 and the internal heat exchanger 8th by means of the first expansion organ 6.1 in the evaporator 3 is relaxed. This is the third expansion organ 6.3 formed bidirectionally, so that it in the flow direction S of the refrigerant circuit 2 is fully open in the cooling mode and ideally a cross-sectional area corresponding to the air conditioning diameter upstream or downstream of the third expansion element 6.3 , having. In this cooling operation, the check valve R2 of the second heat pump branch WPZ2 prevents the refrigerant from overflowing the check valve R2 in the direction of the heater 5.2 can flow.

To 1 becomes the heating register 5.2 operated at high pressure level. If the shut-off valve V2 by a fifth expansion element 6.5 replaced, as in the vehicle air conditioning 1 to 2 is provided, the heating register 5.2 operated at medium pressure. This allows this heater 5.2 be carried out with reduced strength requirements. The pressure-side operating limits for the heating coil 5.2 , are specified in this case on the specification of a low pressure component in terms of the maximum allowable operating pressure and the resulting bursting pressure.

The vehicle air conditioner 1 to 2 differs from the one after 1 in that the check valve R2 of the second heat pump branch WPZ2 does not communicate directly with the third expansion element 6.3 fluidly connected, but with a node, the two expansion organs 6.1 and 6.4 with the internal heat exchanger 8th fluidly. As a result, in the heating mode by means of the second heat pump cycle process, the refrigerant initially flows via the check valve R2 into the internal heat exchanger 8th and only then by means of the third expansion organ 6.3 in the gas cooler 5.1 relaxed. As already noted above, the second shut-off valve V2 is the fifth expansion element 6.5 formed with a shut-off function.

In the refrigerant circuit 2 according to 1 is the internal heat exchanger 8th for the third heat pump branch WPZ3 actively integrated into the process connection and flows through, while in the refrigerant circuit 2 according to 2 whereas the second heat pump branch WPZ2 is active. Due to the changed wiring designed for the refrigerant circuit 2 according to 2 the package situation advantageous for the whole system.

In the vehicle air conditioner 1 to 3 is the second heat pump branch WPZ2 unlike 1 such with the internal heat exchanger 8th connected, that in the heating operation with the second heat pump cycle process by means of the second heat pump branch WPZ2 of the internal heat exchanger 8th is active. Thus, the check valve R2 of the second heat pump branch WPZ2 is directly downstream with the inner heat exchanger 8th fluidly connected, so that only the output of the internal heat exchanger 8th , with which also the two expansion organs 6.1 and 6.4 connected with the third expansion organ 6.3 the second heat pump branch WPZ2 establishes a fluid connection. Thus, in the heating mode by means of the second heat pump cycle process, the refrigerant from the heater 5.2 via the check valve R2, the internal heat exchanger 8th and then by means of the third expansion organ 6.3 in the gas cooler 5.1 relaxed. This is the inner heat exchanger 8th flows through in countercurrent process. The internal heat exchanger 8th is therefore actively involved in the process control both for the second heat pump branch WPZ2 and for the third heat pump branch WPZ3.

The fluid connection between the check valve R2 and the internal heat exchanger 8th is via a check valve R5 directly to the gas cooler 5.1 connected, with which in the cold operation of the vehicle air conditioning 1 the refrigerant from the gas cooler 5.1 via this check valve R5, the internal heat exchanger 8th by means of the first expansion organ 6.1 in the evaporator 3 can be relaxed. In this cooling mode, the third expansion organ 6.3 locked by means of its shut-off function. Also in heating operation with the third heat pump cycle process by means of the third heat pump branch WPZ3 is this third expansion organ 6.3 blocked.

The check valve R5 is arranged so that in the heating operation by means of the first or third heat pump cycle process refrigerant from the check valve R2 of the second heat pump branch WPZ2 not directly into the gas cooler 5.1 can flow.

The vehicle air conditioner 1 according to the 4 to 6 differs from the one according to the 1 to 3 in that the high pressure refrigerant coolant heat exchanger 7 Coolant flows through only in heating mode. For this purpose, the valve assembly V is not downstream of the high-pressure refrigerant-refrigerant heat exchanger 7 but directly after the refrigerant compressor 4 , ie in the flow direction S of the refrigerant circuit 2 before the refrigerant-refrigerant heat exchanger 7 ,

Thus, the first shut-off valve V1 connects the refrigerant compressor 4 via the first shut-off valve V1 downstream third shut-off valve V3 with the gas cooler 5.1 while the second shut-off valve V2 the refrigerant compressor 4 with the high-pressure refrigerant-refrigerant heat exchanger 7 fluidly.

The first heat pump branch WPZ1 fluidly connects the outlet of the high-pressure refrigerant-refrigerant heat exchanger 7 with the refrigerant collector 9 , wherein the fluid connection between the second expansion element 6.2 of the first heat pump branch WPZ1 and the associated check valve R1 via a further shut-off valve V4 with the fluid connection between the first Shut-off valve V1 and the third shut-off valve V3 is fluidly connected.

This branch from the shut-off valve V4 and the subsequent check valve R1 of the first heat pump branch WPZ1 is required for the second heat pump cycle process by means of the second heat pump branch WPZ2. To carry out this second heat pump cycle process, the first shut-off valve V1 is closed and the second shut-off valve V2 is opened, so that the refrigerant from the high-pressure refrigerant-refrigerant heat exchanger 7 over the heating register 5.2 and the check valve R2 by means of the third expansion element 6.3 in the gas cooler 5.1 is relaxed, from which it then via the open third shut-off valve V3, the open shut-off valve V4, the check valve R1, the refrigerant collector 9 and the internal heat exchanger 8th to the refrigerant compressor 4 is returned.

To carry out the first heat pump cycle process by means of the first heat pump branch WPZ1, this shut-off valve V4 must be closed, so that the refrigerant from the refrigerant compressor 4 via the open shut-off valve V2 (with shut-off valve V1 closed) and the high-pressure refrigerant-coolant heat exchanger 7 into the first heat pump branch WPZ1 and via the second expansion element 6.2 , the refrigerant collector 9 and the internal heat exchanger 8th to the refrigerant compressor 4 is returned. For this purpose, the fluid connection of the high-pressure refrigerant-refrigerant heat exchanger 7 or the first heat pump branch WPZ1 to the heater 5.2 by means of a fifth expansion organ 6.5 , which is equipped with a shut-off function, locked. This will be the downstream heating coil 5.2 operated at medium pressure level and can thus be performed with reduced strength requirements. This expansion organ 6.5 can also be designed as a shut-off valve V5.

The heating operation by means of the second heat pump cycle process corresponds to that of the vehicle air conditioning system 1 , For this purpose, when the first shut-off valve V1 is closed, the second shut-off valve V2 is opened and the second expansion element 6.2 the first heat pump branch WPZ1 closed so that refrigerant from the refrigerant compressor 4 via the high-pressure refrigerant-refrigerant heat exchanger 7 , the heating register 5.2 , the check valve R2 with closed expansion organs 6.1 and 6.4 by means of the third expansion organ 6.3 in the gas cooler 5.1 is relaxed. Subsequently, the refrigerant flows via the shut-off valves V3 and V4, the check valve R1, the refrigerant collector 9 and the internal heat exchanger 8th back to the refrigerant compressor 4 ,

The implementation of the third heat pump cycle process is carried out as in the vehicle air conditioning 1 , For this purpose, when the first shut-off valve V1 is closed, the second shut-off valve V2 is opened and the second expansion element 6.2 the first heat pump branch WPZ1 closed so that refrigerant from the refrigerant compressor 4 via the refrigerant-coolant heat exchanger 7 , the heating register 5.2 , the check valve R2, the internal heat exchanger 8th by means of the fourth expansion organ 6.4 in the chiller 10 is relaxed. The third expansion organ 6.3 of the second heat pump branch WPZ2 is locked in this heating mode.

In the heating operation by means of the second and third heat pump cycle process is when using a shut-off valve V5 instead of a fifth expansion element 6.5 operated the heating register at a high pressure level, otherwise at a medium-pressure level, so that the downstream heating coil 5.2 can be performed with reduced strength requirements.

To carry out a cooling operation of the vehicle air conditioner 1 according to 4 For example, the second shut-off valve V2 and the fourth shut-off valve V4 are closed while the first shut-off valve V1 and the third shut-off valve V3 are opened, whereby the refrigerant from the high-pressure refrigerant-refrigerant heat exchanger 7 over the gas cooler 5.1 and the internal heat exchanger 8th by means of the first expansion organ 6.1 in the evaporator 3 is relaxed. This is the third expansion organ 6.3 formed bidirectionally, so that it in the flow direction S of the refrigerant circuit 2 is opened in cooling mode. In this cooling operation, the check valve R2 of the second heat pump branch WPZ2 prevents the coolant via the check valve R2 in the direction of the heating register 5.2 can flow.

The 5 shows a vehicle air conditioning 1 in which, unlike that after 4 the first heat pump branch WPZ1 in the flow direction of the refrigerant circuit 2 not the high-pressure refrigerant-refrigerant heat exchanger 7 is directly downstream, but only after the heater 5.2 branches. To carry out the first heat pump cycle process is an addition to the heater 5.2 downstream shut-off valve V6 locked, so that in the flow direction S of the refrigerant circuit 2 the high-pressure refrigerant from the refrigerant-refrigerant heat exchanger 7 over the heating register 5.2 flows into the first heat pump branch WPZ1, in which the refrigerant by means of the second expansion valve 6.2 Relaxed at low pressure level and via the check valve R1, via the refrigerant collector 9 and the internal heat exchanger 8th to the refrigerant compressor 4 is returned. In the refrigerant circuit 2 according to 5 is between the high-pressure refrigerant-refrigerant heat exchanger 7 and the heating register 5.2 a fifth expansion organ 6.5 switched, causing this heater 5.2 operated at medium pressure level and therefore can be performed with reduced strength requirements. This fifth expansion organ 6.5 can be omitted, with the result of the operation of the heating register 5.2 at high pressure level.

The heating operation by means of the second and third heat pump cycle process corresponds to that of the vehicle air conditioner 1 according to 4 ,

The vehicle air conditioner 1 to 6 differs from the one after 5 in that the high pressure refrigerant coolant heat exchanger 7 and the heating register 5.2 in the air conditioner 1.1 to a single directly condensing and refrigerant cooling and possibly condensing component 5.3 are summarized, so that ideally via direct gas cooling / condensation, the bound heat in the refrigerant can be transferred to the cabin air flow. This component 5.3 has an increasing block depth during the heating heat exchanger 7.2 can be executed with a reduced block depth.

To carry out the second or the third heat pump cycle process, the first shut-off valve V1 is closed while the second shut-off valve V2 is open. This shut-off valve V2 can also be replaced by a fifth expansion element 6.5 replaced, resulting in the combined component 5.3 is not operated at a high pressure level, but at a medium-pressure level and can therefore be carried out with reduced strength requirements.

If that is the component 5.3 downstream shut-off valve V6 bidirectional blocking, the check valve R2 of the second heat pump branch WPZ2 can be omitted.

The vehicle air conditioning system according to the invention 1 is in accordance with the 1 to 6 realized with low component costs in a simple system design, in which the shut-off valves are bidirectionally flowed through and bi-directionally sealed.

LIST OF REFERENCE NUMBERS

1

Vehicle air conditioning

1.1

Air conditioner of the vehicle air conditioner 1

2

Refrigerant circuit of the vehicle air conditioner 1

3

Evaporator of the refrigerant circuit 2

4

Refrigerant compressor of the refrigerant circuit 2

5.1

Refrigerant condenser, gas cooler

5.2

heater

5.3

Heating register, component of high-pressure refrigerant-refrigerant heat exchanger 7 and heating register 5.2

6.1

first expansion organ, expansion valve

6.2

second expansion organ, expansion valve

6.3

third expansion organ, expansion valve

6.4

fourth expansion element, expansion valve

6.5

fifth expansion organ, expansion valve

7 '

High-pressure refrigerant-refrigerant heat exchanger (indirect condenser / gas cooler)

7.1

Heating heat exchanger

7.2

Heating heat exchanger

8th

internal heat exchanger

9

Refrigerant collector or accumulator

10

Low-pressure refrigerant-refrigerant heat exchanger, chiller

11

Heating circuit

12

water pump

13

Heat source of the coolant circuit 14

14

Coolant circuit of the low-pressure refrigerant-refrigerant heat exchanger 10

R1

Check valve of the first heat pump branch WPZ1

R2

Check valve of the second heat pump branch WPZ2

R3

Check valve of third heat pump branch WPZ3

R4

check valve

R5

check valve

S

Flow direction of the refrigerant circuit 2

V

valve assembly

V1

shut-off valve

V2

shut-off valve

V3

shut-off valve

V4

shut-off valve

V5

shut-off valve

V6

shut-off valve

WPZ1

first heat pump branch

WPZ2

second heat pump branch

WPZ3

third heat pump branch

Claims (12)

Vehicle air conditioning system ( 1 ) with a heat pump circuit with a heating function and as a refrigeration cycle with cooling function operable refrigerant circuit ( 2 ), comprising: - an evaporator ( 3 ), a refrigerant compressor ( 4 ), a refrigerant condenser / gas cooler ( 5.1 ), an evaporator ( 3 ) associated first expansion organ ( 6.1 ), - a refrigerant compressor ( 4 ) downstream high-pressure refrigerant coolant heat exchangers ( 7 ) and - one with the high-pressure refrigerant-refrigerant heat exchanger ( 7 ) thermally coupled heating heat exchanger ( 7.1 ) for carrying out the heating function, wherein - for the realization of the heating function, a second expansion element ( 6.2 ) and in the flow direction of the refrigerant circuit ( 2 ) downstream check valve (R1) as the first heat pump branch (WPZ1) are provided, wherein the reversal of the flow direction in the first heat pump branch (WPZ1) is prevented by the check valve (R1), - by means of a valve arrangement (V, V1, V2, V3) of the first Heat pump branch (WPZ1) to form a first heat pump circuit process with the refrigerant compressor ( 4 ) and the high-pressure refrigerant-refrigerant heat exchanger ( 7 ) under the arrangement of the second expansion element ( 6.2 ) in the flow direction of the refrigerant circuit ( 2 ) downstream of the high-pressure refrigerant-refrigerant heat exchanger ( 7 ) is fluidly connected, wherein by means of the first heat pump cycle process, a recovery of the heat absorbed by the refrigerant waste heat of the refrigerant compressor ( 4 ), and - the valve arrangement (V, V1, V2) the high-pressure refrigerant-refrigerant heat exchanger ( 7 ) in the flow direction of the refrigerant circuit ( 2 ), wherein by means of the valve arrangement (V, V1, V2), the refrigerant in the cooling mode via the refrigerant condenser / gas cooler ( 5.1 ) and to realize the heating function by means of the heat pump cycle process via the first heat pump branch (WPZ1) is performed. Vehicle air conditioning system ( 1 ) with a heat pump circuit with a heating function and as a refrigeration cycle with cooling function operable refrigerant circuit ( 2 ), comprising: - an evaporator ( 3 ), a refrigerant compressor ( 4 ), a refrigerant condenser / gas cooler ( 5.1 ), an evaporator ( 3 ) associated first expansion organ ( 6.1 ), - a refrigerant compressor ( 4 ) downstream high-pressure refrigerant coolant heat exchangers ( 7 ) and - one with the high-pressure refrigerant-refrigerant heat exchanger ( 7 ) thermally coupled heating heat exchanger ( 7.1 ) for carrying out the heating function, wherein - to realize the heating function, a second expansion element ( 6.2 ) and in the flow direction of the refrigerant circuit ( 2 ) downstream check valve (R1) as the first heat pump branch (WPZ1) are provided, wherein the reversal of the flow direction in the first heat pump branch (WPZ1) is prevented by the check valve (R1), - by means of a valve arrangement (V, V1, V2, V3) of the first Heat pump branch (WPZ1) to form a first heat pump circuit process with the refrigerant compressor ( 4 ) and the high-pressure refrigerant-refrigerant heat exchanger ( 7 ) under the arrangement of the second expansion element ( 6.2 ) in the flow direction of the refrigerant circuit ( 2 ) downstream of the high-pressure refrigerant-refrigerant heat exchanger ( 7 ) is fluidly connected, wherein by means of the first heat pump cycle process, a recovery of the heat absorbed by the refrigerant waste heat of the refrigerant compressor ( 4 ), and - the valve arrangement (V, V1, V2, V3) the refrigerant compressor ( 4 ) in the flow direction of the refrigerant circuit ( 2 ), wherein by means of the valve arrangement (V, V1, V2, V3), the refrigerant in the cooling mode via the refrigerant condenser / gas cooler ( 5.1 ) and for the realization of the heating function by means of the first heat pump cycle process via the high-pressure refrigerant-refrigerant heat exchanger ( 7 ) and then the first heat pump branch is performed. Vehicle air conditioning system ( 1 ) according to claim 1 or 2, wherein in the flow direction of the refrigerant circuit ( 2 ) a heating register ( 5.2 ) downstream of the high-pressure refrigerant-refrigerant heat exchanger ( 7 ) is arranged. Vehicle air conditioning system ( 1 ) according to claims 2 and 3, wherein the heating register ( 5.2 ) in the flow direction of the refrigerant circuit ( 2 ) upstream with the second expansion element ( 6.2 ) of the first heat pump branch is connected. Vehicle air conditioning system ( 1 ) according to one of the preceding claims, in which in the flow direction of the refrigerant circuit ( 2 ) the first heat pump branch (WPZ1) upstream of an internal heat exchanger ( 8th ), which is connected to the refrigerant compressor ( 4 ) is fluidly connected. Vehicle air conditioning system ( 1 ) according to claim 5, wherein in the flow direction of the refrigerant circuit ( 2 ) the first heat pump branch (WPZ1) upstream of a refrigerant collector ( 9 ) is arranged, which the internal heat exchanger ( 8th ) is connected upstream. Vehicle air conditioning system ( 1 ) according to one of the preceding claims, in which - for the realization of the heating function, a second heat pump branch (WPZ2) by means of the refrigerant condenser / gas cooler ( 5.1 ), one in the flow direction of the refrigerant circuit ( 2 ) upstream of the refrigerant condenser / gas cooler ( 5.1 ) arranged third expansion element ( 6.3 ) and in the flow direction of the refrigerant circuit ( 2 ) upstream of the third expansion element ( 6.3 ) arranged check valve (R2) is provided, wherein the reversal of the flow direction in the second heat pump branch (WPZ2) by the check valve (R2) is prevented, and - by means of the valve arrangement (V, V1, V2, V3), the second heat pump branch (WPZ2) to form a second heat pump cycle process on the one hand in Flow direction of the refrigerant circuit ( 2 ) is connected upstream of the first heat pump branch (WPZ1) or the check valve (R1) of the first heat pump branch (WPZ1) and on the other hand with the refrigerant compressor ( 4 ) and the high-pressure refrigerant-refrigerant heat exchanger ( 7 ) with arrangement of the check valve (R2) in the flow direction of the refrigerant circuit ( 2 ) downstream of the high-pressure refrigerant-refrigerant heat exchanger ( 7 ) is fluidly connected, wherein by means of the second heat pump cycle process, a recovery of the refrigerant by means of the refrigerant condenser / gas cooler ( 5.1 ) absorbed ambient heat is effected. Vehicle air conditioning system ( 1 ) according to claim 7, wherein between the check valve (R2) of the second heat pump branch (WPZ2) and the third expansion element ( 6.3 ) the internal heat exchanger ( 8th ) is attached. Vehicle air conditioning system ( 1 ) according to one of the preceding claims, in which - for the realization of the heating function, a fourth expansion element ( 6.4 ) and in the flow direction of the refrigerant circuit ( 2 ) downstream low-pressure refrigerant-refrigerant heat exchanger ( 10 ) are provided as the third heat pump branch (WPZ3), and - by means of a valve arrangement (V, V1, V2, V3) of the third heat pump branch (WPZ3) to form a third heat pump cycle with the refrigerant compressor ( 4 ) and the high-pressure refrigerant-refrigerant heat exchanger ( 7 ) under the arrangement of the fourth expansion element ( 6.4 ) in the flow direction of the refrigerant circuit ( 2 ) downstream of the high-pressure refrigerant-refrigerant heat exchanger ( 7 ) is fluidly connected, wherein by means of the third heat pump cycle process (WPZ3) a recovery of the coolant by means of the low-pressure refrigerant-refrigerant heat exchanger ( 10 ) absorbed waste heat is caused by electrical components. Vehicle air conditioning system ( 1 ) according to one of the preceding claims, in which the high-pressure refrigerant-refrigerant heat exchanger ( 7 ) a fifth expansion organ ( 6.5 ) is connected downstream. Vehicle air conditioning system ( 1 ) according to one of claims 3 to 10, in which the high-pressure refrigerant-refrigerant heat exchanger ( 7 ) and the heating register ( 5.2 ) functionally in a component ( 5.3 ) are united. Vehicle with a vehicle air conditioning system ( 1 ) according to any one of the preceding claims.

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