AIR CONDITIONING ARRANGEMENT WITH CONTROLLED EJECTOR

Description

[0001] The invention relates to an air conditioning arrangement for heating or cooling a space, in particular a vehicle interior, comprising a compressor for conveying a coolant, and to a motor vehicle with such an air conditioning arrangement.

[0002] Air conditioning systems that use CO2 as a refrigerant are already known. Such air conditioning systems are currently limited in their performance at high outside temperatures. In addition, alternative refrigerants with better performance, such as R1234YF, are being used in air conditioning systems. However, such refrigerants are not environmentally neutral and, depending on the situation, can be flammable and compromise safety. Furthermore, refrigerants such as R1234YF have limited use in heat pump operation.

[0003] US Pat. No. 7,428,826 B2 describes an ejector device that controls a refrigerant flow to a first and a second evaporator. US Pat. No. 7,726,150 B2 also discloses such an ejector device.

[0004] US Pat. No. 7,254,961 B2 discloses a refrigerant circuit with an ejector. The ejector is located downstream of a heat exchanger or condenser and serves as a deceleration device for the refrigerant.

[0005] WO 2018 / 159322 A1 describes an ejector with an adjustable nozzle opening by means of a movable needle.

[0006] JP 2008-082614 A discloses an air conditioning system with an ejector. The air conditioning system has multiple compressors to increase cooling capacity.

[0007] US Pat. No. 7,707,849 B2 discloses a refrigerant circuit with an ejector. The ejector is integrally formed with a first evaporator, a second evaporator, and an adjustment mechanism.

[0008] DE 10 2008 005076 A1 describes a refrigerant circuit provided with a compressor, a condenser or gas cooler, an ejector with a high-pressure connection and a suction connection, a pre-evaporator, a separator with a liquid phase outlet and a gas phase outlet, a low-temperature evaporator arranged between the liquid phase outlet of the separator and the suction connection, and a superheat evaporator arranged between the gas phase outlet of the separator and the suction side of the compressor.

[0009] DE 10 2008 011255 A1 relates to an air conditioning system for a motor vehicle and a method for operating this air conditioning system. The air conditioning system comprises an ejector with a main ejector inlet, a side ejector inlet, and an ejector outlet, as well as an internal heat exchanger with respect to the circulating medium, having a first heat exchanger passage and a second heat exchanger passage, and an accumulator with an accumulator inlet and a first accumulator outlet. The main ejector inlet is connected upstream to the first heat exchanger passage. The ejector outlet is connected downstream to the accumulator inlet.

[0010] CN 103 808 101 B discloses a combined synergistic dual-jet and dual counterflow refrigeration cycle system for a dual-temperature refrigerator. The combined synergistic dual-jet counterflow refrigeration cycle system for the dual-temperature refrigerator is characterized by comprising a compressor, an exhaust counterflow device, a condenser, an intake counterflow device, a first capillary tube, a second capillary tube, a refrigeration chamber evaporator, a first injector, a second injector, a freezing chamber evaporator, and a gas-liquid separator.

[0011] DE 11 2014 002876 T5 describes an ejector cycle in which a high-stage ejector is used as a first decompression section instead of the high-stage throttle device. The high-stage ejector has a high-stage nozzle section and a high-stage body section. The high-stage nozzle section reduces the pressure of a refrigerant. The high-stage body section is formed with a high-stage refrigerant intake port that draws in the refrigerant flowing from a first evaporator and a high-stage diffuser section that increases the pressure of a mixed refrigerant.

[0012] The invention is based on the object of creating an air conditioning system that can efficiently utilize the refrigerant CO2, even for heat pump applications. In particular, the object of the invention is to create an air conditioning system that can be reliably operated using CO2 as a refrigerant, even under extreme climatic conditions.

[0013] This object is achieved by the features specified in claim 1. Further advantageous embodiments of the invention are described in the subclaims.

[0014] The embodiments shown in Figures 1-5 in this description, which are not covered by the claims, are for illustration purposes only.

[0015] According to one aspect of the invention, an air conditioning system for heating or cooling a space, in particular a vehicle interior, is provided. The air conditioning system comprises a compressor for conveying a refrigerant. Preferably, the refrigerant can be CO 2 . However, the air conditioning system is not limited to CO 2 as the refrigerant. In particular, R1234yf, propane, butane, or mixtures of propane and butane, or mixtures of CO 2 and the like can be used as refrigerants by the air conditioning system.

[0016] The air conditioning arrangement further comprises a high-pressure chiller, a low-pressure chiller, a liquid separator or economizer and a controlled first ejector.

[0017] Downstream of the compressor, a high-pressure chiller is located to cool the refrigerant, and upstream of the compressor, a low-pressure chiller is located to heat the refrigerant. Alternatively, a gas cooler and / or an indoor condenser can be installed instead of the high-pressure chiller to perform the corresponding function.

[0018] A refrigerant exiting the high-pressure chiller or the gas cooler and / or the indoor condenser can be fed to a propellant inlet of a first controlled ejector, and a refrigerant exiting the low-pressure chiller can be fed to a suction inlet of the first ejector. Furthermore, an outlet of the first ejector is connected directly or indirectly to a liquid separator.

[0019] According to a further aspect of the invention, a motor vehicle is provided which has an air conditioning arrangement according to the invention.

[0020] The air conditioning system can, for example, be operated as a CO2 air conditioning system, which offers increased efficiency. An electric vehicle equipped with such an air conditioning system can thus benefit from an increased range. The air conditioning system enables the reliable use of CO2 as a refrigerant even under extreme climatic conditions.

[0021] The first ejector is preferably designed as a regulated ejector. A propellant mass flow can be provided at the propellant mass inlet of the first ejector, which propellant mass flow has a higher pressure than a suction mass flow. Thus, in an annular gap between a nozzle and a needle of the ejector, the propellant mass flow can be accelerated by the suction mass flow. After passing through the nozzle, the momentum of the propellant mass flow is transferred to the suction mass flow. Both mass flows mix in the process. In the downstream diffuser of the first ejector, the cross-section increases, reducing the velocity of the resulting total mass flow and increasing the pressure above the level of the suction mass flow. The diffuser forms the outlet of the first ejector.

[0022] By axially shifting the needle relative to the nozzle, the size of the annular gap is adjusted to requirements and boundary conditions. This allows for a variable nozzle cross-section. Proportional magnets with position sensors, stepper motors with spindle drives, DC motors with spindle drives, or actuators based on shape memory alloys can be used as actuators to control the first ejector.

[0023] Preferably, the air conditioning arrangement can be used in combined air conditioning and heat pump systems in electric vehicles or BEVs. In particular, carbon dioxide or CO2 can be used as the refrigerant, which can be used in both air conditioning and heat pump operation.

[0024] Due to the design of the air conditioning system and the properties of CO2, different phase states and phase changes occur within the ejector. This can lead to pressure surges or pulsations. The variability of the nozzle cross-section allows operating points with shock waves or pulsations to be avoided in the 2-phase ejector.

[0025] Furthermore, the air conditioning arrangement can be used to utilize an increased temperature delta between the evaporator or the high-pressure chiller and the condenser or the low-pressure chiller.

[0026] The efficiency of the air conditioning system can be increased if the outlet of the first ejector is indirectly connected to the liquid separator via an interior evaporator. This allows, for example, cooling capacity to be supplied to the vehicle interior before the refrigerant reaches the liquid separator. In the liquid separator, which is preferably designed as a so-called economizer, the refrigerant can be separated into its gaseous and liquid components. The gaseous components of the refrigerant are then conveyed or directed toward the compressor, and the liquid components of the refrigerant are directed toward the low-pressure chiller.

[0027] According to a further embodiment, an interior evaporator is connected in parallel to the low-pressure chiller, with an expansion valve connected upstream of the interior evaporator and / or the low-pressure chiller. By connecting an expansion valve upstream, the flow of the at least partially condensed refrigerant to the low-pressure chiller and / or the interior evaporator can be precisely controlled. In particular, the refrigerant, which is partially or completely in the liquid phase, can be reevaporated in the interior evaporator, thereby generating additional cooling capacity.

[0028] The refrigerant supply to the first ejector can be pre-cooled if a refrigerant outlet of the high-pressure chiller or the gas cooler is thermally coupled to a refrigerant inlet of the compressor, particularly via an internal heat exchanger. This measure also eliminates the need for an optional gas cooler in the front end.

[0029] The low-pressure chiller and the high-pressure chiller are thermally charged with cooling water and heating water, respectively, to heat or cool the refrigerant passing through them. The corresponding heat transfer between the ambient air and the refrigerant thus occurs via the cooling water. The efficiency losses due to heat transfer via the cooling water are compensated by the increased efficiency of the air conditioning system.

[0030] According to the invention, the outlet of the first ejector is indirectly connected to the liquid separator via a second ejector, wherein the outlet of the first ejector is connected to a suction mass inlet of the second ejector, and the outlet of the second ejector is connected to the liquid separator. This measure allows additional components, in particular interior evaporators or interior condensers, to be integrated into the air conditioning system. The second ejector is preferably also designed as a regulated ejector similar to the design of the first ejector. This allows the refrigerant flow to be controlled independently of the first ejector by the additionally integrated component.

[0031] The air conditioning arrangement can be used in a particularly versatile manner since, according to the invention, a branch arranged downstream of the compressor or upstream of the compressor, in particular downstream of the liquid separator, or downstream of the high-pressure chiller is connected via an interior heat exchanger to a propellant inlet of the first ejector or the second ejector.

[0032] According to the invention, the outlet of the first ejector is connected to a propellant inlet of the second ejector, wherein an interior heat exchanger flows through a refrigerant branched off upstream of the low-pressure chiller and is connected to the suction mass inlet of the first ejector; or wherein the interior heat exchanger flows through a refrigerant branched off downstream of the high-pressure chiller and is connected to the suction mass inlet of the second ejector. As a result, the interior heat exchanger can be selectively connected to the high-pressure side or the low-pressure side of the refrigerant in order to supply a heating or cooling capacity to the space, in particular the vehicle interior.

[0033] The air conditioning system can also be optimally used with CO2 as the refrigerant for hot-land applications if a gas cooler can be connected between the refrigerant outlet of the high-pressure chiller and the propellant inlet of the first ejector, or between the refrigerant outlet of the liquid separator and the propellant inlet of the first ejector. Furthermore, the additional gas cooler can also reliably meet increased comfort requirements that require greater cooling capacity.

[0034] According to a further embodiment, a refrigerant outlet of a gas cooler can be connected to the propellant inlet of the second ejector. Depending on the design of the air conditioning system, the gas cooler can, in principle, be used for heat transfer in any direction. Thus, the gas cooler can be used to remove heat from the refrigerant or to add heat to the refrigerant.

[0035] Exemplary embodiments of the invention are explained in more detail below with reference to the drawings. They show: Fig. 1 shows a schematic representation of an air conditioning device according to a first exemplary embodiment, not according to the invention. Fig. 2 shows a schematic representation of an air conditioning device according to a second exemplary embodiment, not according to the invention. Fig. 3 shows a schematic representation of an air conditioning device according to a third exemplary embodiment, not according to the invention. Fig. 4 shows a schematic representation of an air conditioning device according to a fourth exemplary embodiment, not according to the invention. Fig. 5 shows a schematic representation of an air conditioning device according to a fifth exemplary embodiment, not according to the invention. Fig. 6 shows schematic representations of an air conditioning device according to a sixth exemplary embodiment in a cooling mode and in a heating mode. Fig. 7 shows schematic representations of an air conditioning device according to a seventh exemplary embodiment in a cooling mode and in a heating mode.8 schematic representations of an air conditioning device according to an eighth exemplary embodiment in an air conditioning mode and in a heat pump mode, Fig. 9 schematic representations of an air conditioning device according to a ninth exemplary embodiment in an air conditioning mode and in a heat pump mode, Fig. 10 schematic representations of an air conditioning device according to a tenth exemplary embodiment in an air conditioning mode, in a heat pump mode and in a reheat mode, Fig. 11 schematic representations of an air conditioning device according to an eleventh exemplary embodiment in an air conditioning mode and in a heating mode, Fig. 12 schematic representations of an air conditioning device according to a twelfth exemplary embodiment in an air conditioning mode and in a heating mode, and Fig. 13 a side view of a motor vehicle according to the invention according to an exemplary embodiment with an air conditioning device.

[0036] In the figures, the same structural elements have the same reference numerals.

[0037] The Fig. 1 shows a schematic representation of an air conditioning device 10 according to a first exemplary embodiment. The air conditioning arrangement 10 serves to heat or cool an exemplary vehicle interior 110, which in the Fig. 13 is illustrated.

[0038] The air conditioning system 10 has a compressor 11 for conveying a refrigerant. CO2, for example, can be used as the refrigerant. In the illustrated embodiment, the compressor 11 is designed as an electrically driven compressor.

[0039] Downstream of the compressor 10, a high-pressure chiller 12 is provided for cooling the refrigerant or for dissipating heat from the refrigerant to a water cooling circuit (not shown).

[0040] Analogous to the high-pressure chiller 12, a low-pressure chiller 13 is provided upstream of the compressor 10 for heating the refrigerant or for extracting heat output from the thermally coupled water cooling circuit.

[0041] A refrigerant exiting the high-pressure chiller 12 is fed to a propellant mass inlet 22 of a first ejector 21 and a refrigerant exiting the low-pressure chiller 13 is fed to a suction mass inlet 23 of the first ejector 20.

[0042] In the illustrated embodiment, an outlet 24 of the first ejector 21 is indirectly connected to a liquid separator 14 via an interior evaporator 15. The interior evaporator 15 is preferably thermally coupled to the vehicle interior 110 and can be circulated with air, for example, by an interior fan.

[0043] The liquid separator 14 is designed as an economizer and can separate the liquid phase from the gaseous phase of the refrigerant. Accordingly, the gaseous phase can be directed toward the compressor 10 and the liquid phase to the low-pressure chiller 13.

[0044] The first ejector 21 is designed as a controlled ejector and has an electric drive 25. The electric drive 25 serves to adjust a cross-section of an annular gap (not shown), with which the speed or volume flow of the propellant mass flow supplied through the propellant mass inlet 22 is adjusted.

[0045] Furthermore, an expansion valve 16 is arranged between the liquid separator 14 and the low-pressure chiller 13 in order to evaporate and thus cool the refrigerant supplied to the low-pressure chiller 13 in the liquid phase.

[0046] In the Fig. 2 A schematic representation of an air conditioning device 10 according to a second exemplary embodiment is shown. In contrast to the first exemplary embodiment, an internal heat exchanger 17 is provided here, which thermally couples a refrigerant outlet of the high-pressure chiller 12 with a refrigerant inlet of the compressor 11.

[0047] The Fig. 3 shows a schematic representation of an air conditioning device 10 according to a third exemplary embodiment. The air conditioning device 10 according to a third exemplary embodiment is based on the exemplary embodiments already described, but the interior evaporator 15 is arranged parallel to the low-pressure chiller 13. An expansion valve 18 is connected upstream of the interior evaporator 15, analogous to the low-pressure chiller 13.

[0048] Since the interior evaporator 15 is arranged at a new position, the first ejector 21, in particular the outlet 24 of the first ejector 21, can be connected immediately or directly to the liquid separator 14.

[0049] The Fig. 4 shows a schematic representation of an air conditioning device 10 according to a fourth exemplary embodiment, which is based on the second exemplary embodiment. In the fourth exemplary embodiment, analogous to the third exemplary embodiment, the interior evaporator 15 is offset downstream of the liquid separator 14 and parallel to the low-pressure chiller 13. An internal heat exchanger 17 is also present, which thermally couples the refrigerant outlet of the high-pressure chiller 12 with the refrigerant inlet of the compressor 11.

[0050] The Fig. 5 10 illustrates a schematic representation of an air conditioning device 10 according to a fifth exemplary embodiment. The air conditioning device 10 according to the fifth exemplary embodiment is based on the third exemplary embodiment and has an interior condenser 19.

[0051] The interior condenser 19 is arranged downstream of the compressor 11, parallel to the high-pressure chiller 12.

[0052] Furthermore, the outlet 24 of the first ejector 21 opens into a suction mass inlet 33 of a second ejector 31. The interior condenser 19 is connected to a propellant mass inlet 32 of the second ejector 31. An outlet 34 of the second ejector 31 finally opens into the liquid separator 14. Thus, the first ejector 21 is indirectly connected to the liquid separator 14 via the second ejector 31.

[0053] The second ejector 31 is designed as a controlled ejector, analogous to the first ejector 21.

[0054] In the fifth embodiment, a branch A1 arranged downstream of the compressor is indirectly connected via the interior condenser 19 to the propellant mass inlet 22 of the second ejector 31.

[0055] Thus, an interior condenser 19 is arranged parallel to the high-pressure chiller 12 and is designed to heat the supply air of the vehicle interior 110. The second jet pump or second ejector 31 serves to regulate the admission and utilization of the expansion work.

[0056] In the fifth embodiment, heating, cooling and reheating are realized by direct heat transfer from the air conditioning circuit to the indoor air.

[0057] The Fig. 6a and Fig. 6b show schematic representations of an air conditioning device 10 according to a sixth embodiment in a cooling mode and in a heating mode. Fig. 6a shows the air conditioning device 10 in a cooling or air conditioning mode and the Fig. 6b the air conditioning device in a heating mode.

[0058] The sixth embodiment is based on the first embodiment and has been expanded by the second ejector 31 and an interior heat exchanger 40. The interior heat exchanger 40 is arranged parallel to the second ejector 31 and is connected to the propellant inlet 32 of the second ejector 31. In cooling mode, the interior heat exchanger 40 is coupled to the second ejector 31 via the liquid separator 14.

[0059] To implement heating operation, the interior heat exchanger 40 must be connected via a branch A1 located downstream of the compressor. In both operating modes, the interior heat exchanger 40 opens into the propellant inlet 32 of the second ejector 31. An expansion valve 18 is positioned in branch A1.

[0060] The operating modes are switched via two valves 51, 52.

[0061] Optionally, a water heat exchanger (not shown) or an air heater for the interior air can be provided to ensure reheat operation for drying the air in the vehicle interior 110.

[0062] For the sake of simplicity, the exemplary embodiments shown in Figs. 1 to 20 explain the principle using a motor vehicle 100 (see Fig. 21). However, the air conditioning system 10 is not limited to use in motor vehicles 100.

[0063] In the Fig. 7a and the Fig. 7b schematic representations of an air conditioning device according to a seventh embodiment are shown in a cooling mode and in a heating mode. The seventh embodiment essentially corresponds to the sixth embodiment. In particular, the Fig. 7a The operating mode shown for cooling the vehicle interior 110 by means of the interior heat exchanger 40 corresponds to the Fig. 6a .

[0064] The Fig. 7b differs in that a branch A2 downstream of the high-pressure chiller 12 is used to supply the interior heat exchanger 40 with refrigerant and to feed it to the propellant inlet 32 of the second ejector 31.

[0065] In the Fig. 8a and Fig. 8b 1 and 2 are schematic representations of an air conditioning device 10 according to an eighth embodiment in an air conditioning mode and in a heat pump mode. The eighth embodiment is based on the second embodiment and has been supplemented by the second ejector 31, which is arranged parallel to an interior heat exchanger 40. The interior heat exchanger 40 replaces the interior evaporator 15.

[0066] In cooling mode, the interior heat exchanger 40 is supplied with refrigerant via a third branch A3, which is located between the low-pressure chiller 13 and the liquid separator 14. The interior heat exchanger 40 opens into the suction mass connection 23 of the first ejector 21.

[0067] In heat pump operation, which is Fig. 8b As illustrated, the interior heat exchanger 40 is connected in parallel to the propellant mass connection 22 of the first ejector 21 with the propellant mass connection 32 of the second ejector 31. In heat pump operation, the interior heat exchanger 40 can be connected in parallel to the high-pressure chiller 12 via the branch and used to heat the vehicle interior 110.

[0068] In cooling mode of the air conditioning device 10, an expansion valve 18 is connected upstream of the interior heat exchanger 40.

[0069] In the following examples, which are described in the Fig. 9 bis Fig. 12 , additional gas coolers 41 are used. These additional gas coolers 41 can be positioned, for example, in a front end of the motor vehicle 100. Direct heat transfer between the refrigerant and the environment is possible. Depending on the design, an optional internal heat exchanger 17 can also be used.

[0070] In the Fig. 9a and the Fig. 9b 1 and 2 are schematic representations of an air conditioning device 10 according to a ninth exemplary embodiment in an air conditioning mode and in a heat pump mode. The ninth exemplary embodiment is essentially based on the first exemplary embodiment and has been expanded by the gas cooler 41, which is integrated into the refrigerant circuit in series with the refrigerant outlet of the high-pressure chiller 12.

[0071] A refrigerant outlet of the gas cooler 41 is connected both to the propellant inlet 22 of the first ejector 21 and to the refrigerant outlet for liquid refrigerant of the liquid separator 14.

[0072] Preferably, a water heat exchanger (not shown) or an air heater may be provided for the interior air of the vehicle interior 110 in order to ensure the heating and reheat operation for air drying.

[0073] In the illustrated embodiment, three valves or shut-off valves 51, 52, 53 are required to drive the first ejector 21 optionally with the refrigerant exiting from the gas cooler 41 or exiting from the high-pressure chiller 12.

[0074] The Fig. 10a , Fig. 10b and Fig. 10c show schematic representations of an air conditioning device 10 according to a tenth embodiment in an air conditioning mode, in a heat pump mode, and in a reheat mode. The air conditioning device 10 according to the eighth embodiment is based on the third embodiment and, analogous to the tenth embodiment, has three shutoff valves 51, 52, 53 for controlling the connection between the high-pressure chiller 12 or the gas cooler 41 and the first ejector 21.

[0075] Preferably, the respective shut-off valves 51, 52, 53 can be controlled by a control unit 54, which can also control the expansion valves 16, 18, for example.

[0076] In the tenth embodiment, both heating and cooling and reheating are realized by direct heat transfer from the refrigerant circuit to the vehicle interior 110.

[0077] Another expansion valve 18, which is used in heat pump mode, is connected downstream of the gas cooler 41. The coolant flows through the interior condenser 19 via the shut-off valves 51, 52, and 53 in heat pump mode and in reheat mode to provide heat output for the vehicle interior 110.

[0078] During air conditioning operation of the air conditioning device 10, the interior condenser 19 is decoupled from the refrigerant circuit, and only the interior evaporator 15 is used to generate cooling capacity.

[0079] In the Fig. 11a and the Fig. 11b 1 and 2 are schematic representations of an air conditioning device 10 according to an eleventh exemplary embodiment in an air conditioning mode and in a heating mode. The eleventh exemplary embodiment of the air conditioning device 10 is based on the sixth exemplary embodiment. Similarly, depending on whether the interior heat exchanger 40 is supplied with refrigerant via the branch A1 downstream of the compressor 11 or via the liquid separator 14, a heating output or a cooling output can be generated in the interior heat exchanger 40 and dissipated to the vehicle interior 110.

[0080] Due to the additional gas cooler 41, three additional shut-off valves 53, 55, 56 are required in addition to the two existing shut-off valves 51, 52 to control the refrigerant flow.

[0081] The Fig. 12a and Fig. 12b 1 and 2 show schematic representations of an air conditioning device 10 according to a twelfth embodiment in an air conditioning mode and in a heating mode. The twelfth embodiment is based on the seventh embodiment and is also supplemented by the gas cooler 41.

[0082] The interior heat exchanger 40 can optionally be connected in series with the high-pressure chiller 12 in order to heat the vehicle interior 110 in heat pump operation.

[0083] An optional water heat exchanger or an air heater is provided for the interior air to ensure reheat operation for air drying.

[0084] The Fig. 13 shows a side view of a motor vehicle 100 according to the invention according to an exemplary embodiment with an air conditioning device 10 according to the invention. The motor vehicle 100 is preferably designed as an electric vehicle or BEV and has a vehicle interior 110 which can be heated, cooled or dehumidified by the air conditioning device 19. Bezugszeichenliste

[0085] 100Motor vehicle 110Vehicle interior 10Air conditioning device 11Compressor 12High-pressure chiller 13Low-pressure chiller 14Liquid separator 15Indoor evaporator 16Expansion valve 17Internal heat exchanger 18Expansion valve 19Indoor condenser 21First ejector 22Propellant mass inlet of the first ejector 23Suction mass inlet of the first ejector 24Outlet of the first ejector 25Electric drive of the first ejector 31Second ejector 32Propellant mass inlet of the second ejector 33Suction mass inlet of the second ejector 34Outlet of the second ejector 40Interior heat exchanger 41Gas cooler 51Valve / Shut-off valve 52Valve / Shut-off valve 53Valve / Shut-off valve 54Control unit 55Valve / Shut-off valve 56Valve / Shut-off valve A1first junction A2second junction A3third junction

Claims

1. Air-conditioning arrangement (10) for heating or cooling a space, in particular a vehicle compartment (110), having a compressor (11) for conveying a refrigerant, wherein a high-pressure chiller (12) for cooling the refrigerant is arranged downstream of the compressor (11) and a low-pressure chiller (13) for heating the refrigerant is arranged upstream of the compressor (11), wherein a refrigerant exiting the high-pressure chiller (12) can be fed to a drive mass inlet (22) of a first ejector (21) and a refrigerant exiting the low-pressure chiller (13) can be fed to a suction mass inlet (23) of the first ejector (21), wherein the outlet (24) of the first ejector (21) is indirectly connected to the liquid separator (14) via a second ejector (31), wherein the outlet (34) of the second ejector (31) is connected to the liquid separator (14), characterized in that the outlet (24) of the first ejector (21) is connected to a suction mass inlet (33) of the second ejector (31) and a branch arranged downstream of the compressor (11) or a branch arranged upstream of the compressor (11) or a branch arranged downstream of the high-pressure chiller (12) is connected to a drive mass inlet (32) of the second ejector (31) via an indoor heat exchanger (40), so that the indoor heat exchanger (40) can alternatively be connected to the high-pressure side and to the low-pressure side of the refrigerant in order to supply a heat output or a cooling output to the space, in particular the vehicle compartment (10).

2. Air-conditioning arrangement according to claim 1, wherein an indoor evaporator (15) is connected in parallel with the low-pressure chiller (13), wherein an expansion valve (16, 18) is connected upstream of the indoor evaporator (15) and / or the low-pressure chiller (13).

3. Air conditioning arrangement according to one of claims 1 or 2, wherein a refrigerant outlet of the high-pressure chiller (12) or the gas cooler (41) is thermally coupled to a refrigerant inlet of the compressor (11), in particular via an indoor heat exchanger (17).

4. Air-conditioning arrangement according to one of claims 1 to 3, wherein a branch (A1) arranged downstream of the compressor (11) is connected in a heating mode via the indoor heat exchanger (40) to a drive mass inlet (32) of the second ejector (31) and in a cooling mode a branch arranged upstream of the compressor is connected via the indoor heat exchanger (40) to the drive mass inlet (32) of the second ejector (31).

5. Air-conditioning arrangement according to one of claims 1 to 3, wherein in a heating mode a branch (A2) arranged downstream of the high-pressure chiller (12) is connected via the indoor heat exchanger (40) to the drive mass inlet (32) of the second ejector (31) and in a cooling mode a branch arranged upstream of the compressor is connected via the indoor heat exchanger (40) to the drive mass inlet (32) of the second ejector (31).

6. Air-conditioning arrangement according to one of claims 1 to 3, wherein in a cooling mode a refrigerant (A3) branched off upstream of the low-pressure chiller (13) flows through the indoor heat exchanger (40) and is connected to the suction mass inlet (23) of the first ejector (21); and wherein, in a heating mode, a refrigerant branched off downstream of the high-pressure chiller (12) flows through the indoor heat exchanger (40) and is connected to the drive mass inlet (32) of the second ejector (31).

7. Air conditioning arrangement according to one of claims 1 to 5, wherein a gas cooler (41) can be connected between the refrigerant outlet of the high-pressure chiller (12) and the drive mass inlet (22) of the first ejector (21) or between the refrigerant outlet of the liquid separator (14) and the drive mass inlet (22) of the first ejector (21).

8. Air conditioning arrangement according to one of claims 1 to 7, wherein a refrigerant outlet of a gas cooler (41) can be connected to the drive mass inlet (32) of the second ejector (31).

9. Motor vehicle (100) having an air conditioning arrangement (10) according to one of the preceding claims.