Refrigeration device with heat pump function based on an expandable base system and motor vehicle with such a refrigeration device

Abstract

The invention relates to a refrigeration device (10) with heat pump function for a motor vehicle, having a basic system (100) embodied in a minimal configuration, comprising: a refrigerant compressor (12); a directly or indirectly acting external heat exchanger (18) arranged downstream of the refrigerant compressor; a directly or indirectly acting first evaporator (22) as part of an air conditioning device (32) for air conditioning of an interior space of the motor vehicle, the first evaporator being arranged downstream of the external heat exchanger (18) and a first expansion mechanism (AE2) being connected upstream of the first evaporator; a second evaporator (28), in particular a cooler, as part of a cooling device for an electric drive unit or an electrical storage unit, the second evaporator being arranged in flow-technical parallel to the first evaporator (22) and a second expansion mechanism (AE1) being connected upstream of the second evaporator; at least one low-pressure-side collector (24) arranged downstream of the first and second evaporators (22, 28) or at least one high-pressure-side collector (25) arranged downstream of the external heat exchanger (18) and upstream of the first and second evaporators (22, 28), wherein the basic system (100) forms a main line (14) and can be connected in flow-technical terms with a secondary line (16) for implementing a heat pump function, the secondary line branching off from the basic system (100) downstream of the refrigerant compressor (12) and having a heating regulator (26) for directly or indirectly heating air, which is part of the air conditioning device (32).

Description

TECHNICAL FIELD

[0001] The invention relates to a refrigeration device with heat pump function for a motor vehicle, having

[0002] a basic system implemented in a minimum configuration, comprising

[0003] a refrigerant compressor;

[0004] a directly or indirectly acting external heat exchanger arranged downstream of the refrigerant compressor;

[0005] a directly or indirectly acting first evaporator as part of an air conditioning device for interior space air conditioning of the motor vehicle, which is arranged downstream of the external heat exchanger and a first expansion mechanism is connected upstream of the first evaporator;

[0006] at least one second evaporator, in particular a chiller, as part of a cooling device for an electric drive unit or an electrical storage unit, which is arranged in parallel in terms of flow technology to the first evaporator and a second expansion mechanism is connected upstream of the second evaporator;

[0007] a single low-pressure-side collector / accumulator arranged downstream of the first and second evaporator or a single high-pressure-side collector arranged downstream of the external heat exchanger and upstream of the first and second evaporator. BACKGROUND

[0008] Heat pump applications for motor vehicles are known, for example, from DE 10 2013 206 626 A1, DE 196 44 583 B4 and DE 10 2012 222 594 A1.

[0009] The applicant himself has filed a number of applications in which different operating methods or reheat methods for complex refrigeration devices of motor vehicles are proposed.

[0010] The refrigeration devices for motor vehicles known to date generally have a very complex structure in order to be able to carry out the desired operating methods in an energy-saving manner. SUMMARY

[0011] It is an object of the invention to specify a simplified refrigeration device with which an energy-saving operation, in particular a reheat operation, can be realized.

[0012] This object is achieved by a refrigeration device having the features of claim 1 and a motor vehicle having the features of claim 12. Advantageous design variants with suitable refinements are specified in the dependent claims.

[0013] Therefore, a refrigeration device with heat pump function for a motor vehicle is proposed, which has

[0014] a basic system implemented in a minimum configuration, which basic system comprises

[0015] a refrigerant compressor;

[0016] an external heat exchanger working directly or indirectly downstream of the refrigerant compressor;

[0017] a first evaporator as part of an air conditioning device for air conditioning of an interior space of the motor vehicle, which first evaporator is arranged downstream of the external heat exchanger and a first expansion mechanism is connected upstream of the first evaporator;

[0018] at least one second evaporator, in particular a cooler, as part of a cooling device for an electric drive unit or an electrical storage unit, which second evaporator is arranged in parallel flow-technically to the first evaporator and a second expansion mechanism is connected upstream of the second evaporator;

[0019] at least one low-pressure-side collector arranged downstream of the first and second evaporators or at least one high-pressure-side collector arranged downstream of the external heat exchanger and upstream of the first and second evaporators.

[0020] It is provided here that the basic system forms a main line and can be connected in flow-technically to a secondary line for the heat pump function, which secondary line branches off from the basic system downstream of the refrigerant compressor and has a second heat exchanger working as a heat source, in particular a heating register, for directly or indirectly heating air, which is part of the air conditioning device.

[0021] In such a refrigeration device, the basic system forms a refrigeration circuit (AC circuit), in which the first evaporator serves for cooling the air delivered to the vehicle interior. The basic system or refrigeration circuit is now supplemented by a sub-circuit, which is of simple construction and in which a heating regulator is arranged. The second heat exchanger, in particular the heating regulator, can be used here for direct or indirect heating of the interior air. Here, this simple implementation of the refrigeration device with heat pump function can in particular be operated in the case of the availability of heat at the second evaporator (cooler), which is usually generated by waste heat of an electric drive unit or an electrical storage unit. It is also possible that, in a supplementary heating or reheating operating mode, the heat deficit in the air conditioning of the interior is made up by the second evaporator (cooler). A reheating operating mode can also be implemented in which the heat demand at the second heat exchanger (heating regulator) and the cooling power at the first evaporator, together with the refrigerant compressor drive power and the heat transferred to the refrigerant thereby, are balanced or regulated in such a way that the air delivered to the interior substantially meets the interior requirements, i.e. the interior does not have to be further heated or cooled at the moment.

[0022] Downstream of the refrigerant compressor, a valve device can be provided in the refrigeration device, which is designed to regulate the flow of refrigerant selectively to the main circuit or / and to the sub-circuit. Thereby, a selective switching to cooling or heating of the interior can be selected.

[0023] The refrigeration device can have an internal heat exchanger, to which a high-pressure-side collector is connected upstream on the high-pressure side, or a low-pressure-side collector is connected upstream on the low-pressure side.

[0024] Downstream of the second heat exchanger, in particular the heating regulator, and upstream of the first expansion mechanism, at least one non-return valve or shut-off valve can be arranged and / or regulated, so that refrigerant can selectively flow from the sub-circuit to the main circuit and refrigerant is prevented from flowing from the main circuit to the sub-circuit.

[0025] Downstream of the first evaporator, a low-pressure-side branch point can be arranged which is connected to a suction section, wherein refrigerant can be sucked from the main circuit and / or from the sub-circuit by means of the suction section. Thereby, it is ensured that refrigerant can be sucked from the non-operating circuit in order to prevent a refrigerant deficit in the operating circuit or refrigerant circuit section.

[0026] Here, a non-return valve can be provided between the first evaporator and the low-pressure-side branch point, which prevents refrigerant from flowing back to the first evaporator.

[0027] A non-return valve can be arranged in the main circuit downstream of the external heat exchanger in such a way that refrigerant, which is in particular introduced from the sub-circuit into the main circuit, can be prevented from flowing back to the external heat exchanger.

[0028] Downstream of the second heat exchanger, in particular the heating regulator, an expansion device can be provided in the secondary line, wherein the expansion device is connected upstream of the external heat exchanger.

[0029] Downstream of the high-pressure collector, a bypass line with an expansion device can branch off, wherein the bypass line ends between a non-return valve and the external heat exchanger, wherein the non-return valve is arranged between the high-pressure collector and the external heat exchanger. Here, the mentioned non-return valve can also be replaced by a shut-off device which is opened or closed depending on the operating mode. This embodiment is particularly recommended for implementing the air heat pump operating mode.

[0030] The refrigeration device can be designed for operating in a reheat operating mode, in which the refrigerant, starting from the refrigerant compressor, flows successively through the following components of the refrigeration device: the second heat exchanger, in particular the heating regulator, in the secondary line, and the evaporator in the main line.

[0031] Furthermore, the refrigeration device can be designed for operating in a triangle process, in which the refrigerant, starting from the refrigerant compressor, flows successively through the following components of the refrigeration device: the second heat exchanger, in particular the heating regulator, in the secondary line, and the second evaporator in the main line, in the presence of a coolant in the cooling device assigned to the second evaporator.

[0032] The refrigeration device described above can be designed for selectively or in series or in parallel adjusting the air heat pump operating mode and / or the water heat pump operating mode in the presence of a low-pressure-side collector in order to provide heat for the cabin air supply.

[0033] The refrigeration device described above can be designed for selectively or in parallel adjusting the air heat pump operating mode and / or the water heat pump operating mode in the presence of a high-pressure collector in order to provide heat for the cabin air supply.

[0034] In the refrigeration device, the base system can be configured as a basic module which can be coupled and / or connected and / or integrated with at least one expansion module which has at least the secondary line and the second heat exchanger, in particular the heating regulator. Thereby, the possibility of a modular construction of the refrigeration device arises. Here, the refrigeration device can be adapted in a simple manner, for example, depending on the vehicle type and other configurations of the motor vehicle, and expanded to have simple or more possible heat pump functions.

[0035] The motor vehicle can be embodied with the refrigeration device described above, in particular an electrically or partially electrically driven motor vehicle. BRIEF DESCRIPTION OF DRAWINGS

[0036] Further advantages and details of the present application result from the following description of embodiments with reference to the drawings.

[0037] Herein is shown:

[0038] Figure 1 A schematic simplified circuit diagram of a basic system of a refrigeration appliance with low-pressure side collector is shown;

[0039] Figure 2 A first extension level of a refrigeration appliance with heat pump function based on the basic system of Figure 1 is shown;

[0040] Figure 2A A further extension level of a refrigeration appliance with heat pump function based on the basic system of Figure 1 is shown;

[0041] Figure 3 A further extension level of a refrigeration appliance with heat pump function based on the basic system of Figure 1 is shown;

[0042] Figure 3A A further extension level of a refrigeration appliance with heat pump function based on the basic system of Figure 1 is shown;

[0043] Figure 4 A further extension level of a refrigeration appliance with heat pump function based on the basic system of Figure 1 is shown;

[0044] Figure 4A A further extension level of a refrigeration appliance with heat pump function based on the basic system of Figure 1 is shown;

[0045] Figure 5 A schematic simplified circuit diagram of a basic system of a refrigeration appliance with high-pressure side collector is shown;

[0046] Figure 6 A first extension level of a refrigeration appliance with heat pump function based on the basic system of Figure 5 is shown;

[0047] Figure 7 A further extension level of a refrigeration appliance with heat pump function based on the basic system of Figure 5 is shown;

[0048] Figure 8 A further extension level of a refrigeration appliance with heat pump function based on the basic system of Figure 5 is shown;

[0049] Figure 9 A further extension level of a refrigeration appliance with heat pump function based on the basic system of Figure 5Another expansion level of a refrigeration device with heat pump function of the base system. DETAILED DESCRIPTION

[0050] Figure 1 An embodiment of a refrigeration device 10 for a motor vehicle is shown schematically and simplified. The refrigeration device 10 comprises a refrigerant circuit 11 which can be operated in a refrigeration device operating mode, also referred to as AC operating mode for short. The refrigeration device 10 comprises a refrigerant compressor 12, an external heat exchanger 18 acting directly or indirectly, a first evaporator 22 and a refrigerant collector 24 on the low-pressure side (low-pressure reservoir). A first expansion mechanism, in particular an expansion valve AE2, is connected upstream of the first evaporator 22. From a branching point Ab1, a second evaporator 28 (chiller) is arranged in parallel in flow technology with the first evaporator 22. A second expansion mechanism, in particular an expansion valve AE1, is connected upstream of the second evaporator 28. On the low-pressure side, the outlet of the second evaporator or chiller 28 again opens into the refrigerant circuit 11 at a branching point Ab2.

[0051] The first evaporator 22 is assigned to an air conditioning device 32 for interior space air conditioning of the motor vehicle. The second evaporator 28 is part of a not further shown cooling device of an electric drive unit or an electrical storage unit of the motor vehicle, in particular the chiller 28 can be used for cooling a battery and / or an electric machine. The cooling device is represented in Figure 1 simplified by a coolant line 28.2, in which a coolant, for example a water-glycol mixture, can be circulated between the chiller 28 and the electrical components to be cooled.

[0052] The evaporator 22 is shown here exemplarily as a front evaporator for the vehicle. The evaporator 22 also represents other possible evaporators in the vehicle, for example a rear evaporator, which can be arranged in parallel in flow technology with one another. In other words, the refrigeration device 10 comprises at least one evaporator 22 (provided for interior space air conditioning).

[0053] The refrigeration device can optionally have an internal heat exchanger 20, which is shown in Figure 1 dashed lines in the figure.

[0054] Figure 1 The refrigeration device 10 shown represents a base system 100 with a low-pressure side collector 24, which is designed for cooling the vehicle interior space by means of the first evaporator 22 and for cooling the vehicle electrical components by means of the second evaporator 28 (chiller). In the base system, the external heat exchanger 18 is configured as a condenser or gas cooler. The base system 100 can also be referred to as an AC system. Figure 1 The circuit course or topology refrigerant circuit shown is subsequently also referred to as main circuit 14. In this example, the collector 24 is provided as the only low-pressure side collector.

[0055] Figure 2 The refrigeration device 10 with a low-pressure side with a refrigerant collector 24 and a simple heat pump function, in particular a water heat pump function, is shown schematically and simplified. In this design, the refrigerant circuit 11 is divided after the refrigerant compressor 12 into the already mentioned main line 14 and a secondary line 16. The secondary line begins at an exemplary branching point Ab3. The secondary line leads into the main line 14 or the base system 100 again at a branching point Ab4.

[0056] The refrigeration device 10 also comprises a second heat exchanger, in particular a heating regulator 26 (also referred to as a heating condenser or a heating gas cooler), which serves as a heat source. A shut-off valve A3 is arranged upstream of the second heat exchanger or heating regulator 26. A non-return valve R4 is arranged downstream of the second heat exchanger or heating regulator 26. The second heat exchanger or heating regulator 26 is part of an air conditioning device 32. Subsequently, the second heat exchanger is referred to as a heating regulator in a corresponding simplified manner, but this does not limit the use of other components as a heat source as a second heat exchanger.

[0057] As already mentioned, the cooler 28 can be used, for example, for cooling electrical components of a vehicle. However, in the embodiment shown here, the cooler can also be used to implement a water heat pump function in the event of the use of waste heat of at least one electrical component.

[0058] A non-return valve R3 is provided between the branching point Ab4 and the external heat exchanger 18. The non-return valve R3 prevents refrigerant flowing in from the secondary line 16 at the branching point Ab4 from entering the external heat exchanger 18, so that the refrigerant is always directed in the direction of the first evaporator 22 and / or the second evaporator 28.

[0059] Between the secondary line 16 and the low-pressure side of the main line 14, a connecting line 13 is present, in which a shut-off valve A5 is arranged. The connecting line extends between the branching points Ab2 and Ab5. Furthermore, a non-return valve R2 is provided in the connecting line 13. The connecting line is used, in particular, to extract or pump refrigerant from the secondary line 16, which is closed by means of the shut-off valve A3, when a refrigerant deficiency occurs in the main line when operating in AC.

[0060] By opening or closing the two shut-off valves A3 and A4, the refrigerant delivered by the refrigerant compressor 12 can be selectively guided into the main line 14 or the secondary line 16. If the refrigerant flow is guided into the secondary line 16, for example, with the shut-off valve A4 closed (shut-off valve A3 open), the compressed hot refrigerant flows to the heating regulator 26. The heating regulator 26 then serves as a heat source, where the air for the interior space ventilation of the vehicle can be heated directly or indirectly. When the shut-off valve A3 is open, the shut-off valve A5 in the connection line 13 is closed. In such a connection, the refrigerant is first guided through the secondary line 16 and the heating regulator 26 and then into the main line again at Ab4, so that, when a refrigerant deficiency occurs during heating operation, refrigerant can be extracted or pumped as required from the connection section 14.1, which extends between the shut-off valve A4 and the non-return valve A3 and has the external heat exchanger 18.

[0061] Figure 2 The refrigeration device shown shows a simple embodiment with a heat pump function. Here, the basic system 100 (see Figure 1 ) is mainly only supplemented by the heating regulator 26 (heat source) for interior space air heating and a plurality of single valves A2 to A5, which enable switching between AC operating mode and heating or heat pump operating mode, together with the corresponding opening (A2 or A5) of the suction from the other non-operating line. It is pointed out that instead of the individual shut-off valves A2 to A5 shown here, a correspondingly embodied multi-way valve can also be used. The multi-way valve is then designed such that A4 and A5 are opened and closed simultaneously and A2 and A3 are opened and closed simultaneously, so that the compressed refrigerant from the refrigerant compressor is guided into the main line 14 or the secondary line 16, respectively, and the suction from the respective other line can be achieved.

[0062] For example, Figure 2 The refrigeration device shown with a heat pump function can be operated in the event of heat available at the second evaporator 28 (cooler), which is usually generated by waste heat of the electrical storage or electrical drive components. Furthermore, the refrigeration device 10 can be operated in a supplementary heating or re-heating operating mode, in which the heat deficiency is made up by the second evaporator 28 (cooler). Finally, the refrigeration device 10 in this configuration can be operated heat budget neutrally even in the re-heating operating mode.

[0063] If there is no air flow at the cooler 28, a delta process can be achieved by the cooler, whereby the refrigerant flows from the second heat exchanger (heater regulator) 26 via the expansion mechanism AE1, the cooler 28 and via the branch point Ab2 to the refrigerant compressor 12.

[0064] Figure 2AFig. 1 shows a refrigeration device with a heat pump function in accordance with Figure 2 a slightly changed embodiment. In this example, the shut-off valve A3 Figure 2 is replaced by an expansion mechanism or expansion valve AE3. Thereby, the refrigeration device 10 can be connected in air heat pump operating mode, if at least one sub-flow of refrigerant from the second heat exchanger (heating regulator) 26 is delivered to the outside heat exchanger via the expansion mechanism AE3 with pressure reduction.

[0065] If no air flow is present at the outside heat exchanger 18, a delta process can also be realized by this outside heat exchanger, wherein refrigerant flows from the second heat exchanger (heating regulator) 26 via the expansion mechanism AE3, the outside heat exchanger 18 and the opened shut-off valve A2 to the refrigeration compressor 12.

[0066] Figure 3 Fig. 1 shows a refrigeration device 10, wherein the heat pump function according to the configuration of Figure 2 is still feasible and wherein in the re-heating operating mode a surplus heat output can also be realized.

[0067] To this end, the sub-line is prolonged downstream of the heating regulator 26 and has an expansion valve AE4, which is connected upstream of the outside heat exchanger 18. Between the branching point Ab4 and the branching point Ab1 a shut-off valve A1 is provided. Fig. 1 shows a refrigeration device 10 with a heat pump function in accordance with Figure 2 In this embodiment, which is expanded compared to Fig. 1, a surplus heat can be output in the supplementary heating or re-heating operating mode by the expansion valve AE4 and the outside heat exchanger 18. At this point, the shut-off valves A2 and A4 are closed. The refrigerant then flows from the outside heat exchanger 18 further in the direction of the first evaporator 22 or the second evaporator (cooler) 28.

[0068] Figure 3A Fig. 1 shows a variant of the refrigeration device 10 according to Figure 3 In this case, the shut-off valve A2 is arranged in flow technology on the other side of the outside heat exchanger 18. In other words, the shut-off valve A2 or the provided branching point Ab6a is arranged downstream of the outside heat exchanger 18. Thereby, in principle an air heat pump operating mode can be realized by the expansion mechanism AE4 and the non-return valve R3. But additionally, in the case that air is present at the outside heat exchanger 18 and the air throughflow in its operation is prevented, a delta process can also be realized.

[0069] Figure 4 Fig. 1 shows a refrigeration device 10, wherein the heat pump function according to the configuration of Figure 2 or Figure 3 is still feasible and wherein additionally an air heat pump function can be realized. To this end, similar toFigure 2 Instead of the non-return valve R3, a further expansion device AE3 is provided. When the shut-off valve Al is open and the expansion valve AE4 is closed, the air heat pump connection is achieved. Correspondingly, the refrigerant from the heating regulator 26 can be delivered via the (partially) open expansion valve AE3 to the external heat exchanger 18. In parallel flow-technically thereto, the refrigerant can be delivered to the first evaporator 22 and / or the second evaporator 28. After passing the external heat exchanger 18, the refrigerant flows back in the direction of the low-pressure refrigerant collector 24 in the case of the shut-off valve A2 being open.

[0070] Figure 4A A variant of the refrigeration device 10 according to Figure 4 is shown. Here, the shut-off valve A2 is arranged flow-technically on the other side of the external heat exchanger 18. In other words, the shut-off valve A2 or the assigned branch point Ab6a is arranged downstream of the external heat exchanger 18. Thereby, in principle, the air heat pump operating mode can be achieved by AE4 and R3. But additionally, in the case of air being present at the external heat exchanger 18, the delta process can also be achieved. If a shut-off device in the form of a non-return valve R3 is used instead of the expansion device AE3, a series connection of the air heat pump and the water heat pump can also be achieved by the heat exchangers 18 and 28, which enables, in addition to the same low-pressure level in the cooler 28 as compared to the heat exchanger 18, a lower pressure level to be adjusted by throttling of AE1, which itself can be advantageous at system start-up.

[0071] The above-described refrigeration device 10 with a low-pressure collector 24, in particular Figures 2 to 4A achieves a selective or series or parallel water heat pump operating mode (by the cooler 28) and / or air heat pump operation (by the external heat exchanger 18) depending on the selected connection, in order to provide heat for the cabin air supply.

[0072] In Figure 5An embodiment of a refrigeration device 10 for a motor vehicle is shown in a schematic and simplified manner. The refrigeration device 10 comprises a refrigerant circuit 11 which can be operated in a refrigeration device operating mode, also referred to simply as AC operating mode. The refrigeration device 10 comprises a refrigerant compressor 12, an external heat exchanger 18, a first evaporator 22 and a high-pressure-side refrigerant collector 25 (high-pressure collector). A first expansion valve AE2 is connected upstream of the first evaporator 22. Starting from a branch point Ab1, a second evaporator 28 (chiller) is arranged in parallel flow-technically with the first evaporator 22. A second expansion valve AE1 is connected upstream of the second evaporator 28. On the low-pressure side, the outlet of the second evaporator or chiller 28 again opens into the refrigerant circuit 11 at a branch point Ab2. The branch point Ab2 is located here downstream of the internal heat exchanger 20.

[0073] The first evaporator 22 is assigned to an air-conditioning apparatus 32 for interior space air conditioning of the motor vehicle. The second evaporator 28 is part of a not further shown cooling device of an electric drive unit or of an electrical storage unit of the motor vehicle, in particular, the chiller 28 can be used for cooling a battery and / or an electric machine. The cooling device is in Figure 1 simplified by a coolant line 28.2, in which a coolant, for example a water-glycol mixture, can be circulated between the chiller 28 and the electrical components to be cooled.

[0074] The evaporator 22 is here shown exemplarily as a front evaporator of the vehicle. The evaporator 22 also represents other possible evaporators in the vehicle, for example a rear evaporator, which can be arranged parallel flow-technically to one another. In other words, the refrigeration device 10 comprises at least one evaporator 22 (provided for interior space air conditioning).

[0075] Figure 5 The refrigeration device 10 shown shows a base system 100 with a high-pressure-side collector 25 which is designed for cooling the vehicle interior space by means of the first evaporator 22 and for cooling the vehicle electrical components by means of the second evaporator 28 (chiller). In the base system, the external heat exchanger 18 is configured as a condenser. The base system 100 can also be referred to as an AC system. Figure 5 The line course or topology refrigerant circuit shown is subsequently also referred to as main line 14. In this example, the collector 25 is provided as the only low-pressure-side collector.

[0076] Figure 6The refrigeration device 10 with a high-pressure side refrigerant collector 25 and a simple heat pump function, in particular a water heat pump function, is shown schematically and simplified. In this design, the refrigerant circuit 11 is divided after the refrigerant compressor 12 into the already mentioned main line 14 and a secondary line 16. The secondary line begins at an exemplary branching point Ab3. The secondary line leads again into the main line 14 or the base system 100 at the branching point Ab4.

[0077] The refrigeration device 10 also comprises a heating regulator 26, also referred to as a heating condenser. Upstream of the heating regulator 26, a shut-off valve A3 is arranged. Downstream of the heating regulator 26, a non-return valve R4 is arranged. The heating regulator 26 is part of the air conditioning device 32.

[0078] As already mentioned, the cooler 28 can be used, for example, to cool electrical components of the vehicle. However, in the embodiment shown here, the cooler can also be used to implement a water heat pump function in the event of the use of waste heat of at least one electrical component.

[0079] A non-return valve R3 is arranged between the branching point Ab4 and the external heat exchanger 18. The non-return valve R3 prevents refrigerant flowing in from the secondary line 16 at the branching point Ab4 from entering the external heat exchanger 18, so that the refrigerant is always directed in the direction of the first evaporator 22 and / or the second evaporator 28.

[0080] Between the secondary line 16 and the low-pressure side of the main line 14, a connecting line 13 is present, in which a shut-off valve A5 is arranged. The connecting line extends between the branching points Ab5 and Ab9. Furthermore, a non-return valve R2 is provided in the connecting line 13. The connecting line is used, in particular, to extract or draw off refrigerant from the secondary line 16, which is closed by means of the shut-off valve A3, when a refrigerant deficiency occurs in the main line when in AC operation.

[0081] By opening or closing the two shut-off valves A3 and A4, the refrigerant delivered by the refrigerant compressor 12 can be selectively directed into the main line 14 or the secondary line 16. If the refrigerant flow is directed to the secondary line 16 when the shut-off valve A4 is closed, for example (shut-off valve A3 open), the compressed hot refrigerant flows to the heating regulator 26. The heating regulator 26 then serves as a heat source, where air for the interior space ventilation of the vehicle can be heated directly or indirectly. When the shut-off valve A3 is open, the shut-off valve A5 in the connecting line 13 is closed. In such a connection, the refrigerant is first directed through the secondary line 16 and the heating regulator 26 and then leads again into the main line at Ab4, from which refrigerant can be extracted or drawn off as required when a refrigerant deficiency occurs during the heating operating mode from the connecting section 14.1, which extends between the shut-off valve A4 and the non-return valve A3 and has the external heat exchanger 18.

[0082] Figure 6 The illustrated refrigeration appliance shows a simple configuration with heat pump functionality. Here, the basic system 100 (cf. Figure 5 ) is mainly only supplemented by a heating regulator 26 (heat sink ) for interior space air heating and a plurality of single valves A2 to A5, which enable switching between AC operating mode and heating or heat pump operating mode, together with the corresponding opening of the suction of the other, non-operating line (A2 or A5). It is pointed out that instead of the individual shut-off valves A2 to A5 shown here, a correspondingly embodied multi-way valve can also be used. The multi-way valve is then designed such that A4 and A5 are opened and closed simultaneously and A2 and A3 are opened and closed simultaneously, so that the compressed refrigerant from the refrigerant compressor is guided into the main line 14 or the secondary line 16, respectively, and the suction from the respective other line can be achieved.

[0083] For example, Figure 6 The illustrated refrigeration appliance with heat pump functionality can be operated in the case of heat available at the second evaporator 28 (chiller), which is usually generated by waste heat of the electrical storage or electrical drive components. Furthermore, the refrigeration appliance 10 can be operated in a supplementary heating or re-heating operating mode, in which the heat deficit is made up by the second evaporator 28 (chiller). Finally, the refrigeration appliance 10 in this configuration can be operated in heat budget balance even in the re-heating operating mode.

[0084] Figure 7 The refrigeration appliance 10 is shown in a simplified and schematic illustration, wherein the heat pump functionality according to the configuration of Figure 6 is still possible and wherein a surplus heat output can also be achieved.

[0085] To this end, the secondary line is extended downstream of the heating regulator 26 and has an expansion valve AE4, which is connected upstream of the external heat exchanger 18. A shut-off valve A1 is provided between the branching point Ab4 and the branching point Ab10. In this extended embodiment of the refrigeration appliance 10 with heat pump functionality compared to Figure 6 , a surplus heat can be output in a supplementary heating or re-heating operating mode by the expansion valve AE4 and the external heat exchanger 18. Here, the shut-off valves A2 and A4 are closed. The refrigerant then flows from the external heat exchanger 18 further in the direction of the first evaporator 22 or the second evaporator (chiller) 28.

[0086] Figure 8 The refrigeration appliance 10 is shown in a simplified and schematic illustration, wherein the heat pump functionality according to the configuration of Figure 6 or Figure 7The heat pump function of the configuration is still feasible, and in addition, an air heat pump function can be realized. For this purpose, an additional expansion valve AE5 is provided instead of the check valve R3. In addition, an additional stop valve A6 is provided in parallel with the stop valve A1 in terms of flow technology. When the stop valve A6 is open and the expansion valve AE4 and the stop valve A1 are closed, the air heat pump connection is realized. Accordingly, the refrigerant from the heating regulator 26 can be delivered to the external heat exchanger 18 via the open stop valve A6 and the (partially) opened expansion valve AE5. In parallel with this in terms of flow technology, the refrigerant can be delivered to the first evaporator 22 and / or the second evaporator 28. After the refrigerant passes through the external heat exchanger 18, the refrigerant flows back in the direction of the refrigerant compressor 12 when the stop valve A2 is open.

[0087] Figure 9 A simplified and schematic illustration shows a refrigeration device 10, wherein according to Figure 8 The heat pump function of the configuration, that is, the air heat pump function is still feasible. A check valve R3 (such as Figure 7 As shown), to replace the stop valve A6 and expansion valve AE5 ( Figure 8 ). In addition, a bypass line with an expansion valve AE6 branches off after the high-pressure collector 25, wherein the bypass line ends between the non-return valve R3 and the external heat exchanger. When the stop valve A1 is open and the expansion valve AE4 is closed, an air heat pump connection is realized (in parallel with the water heat pump function). Accordingly, the refrigerant from the heating regulator 26 can be conveyed to the external heat exchanger 18 via the open stop valve A1 and the (partially) open expansion valve AE6. In parallel with this, the refrigerant can be conveyed to the first evaporator 22 and / or the second evaporator 28 in terms of flow technology. After the refrigerant has passed through the external heat exchanger 18, it flows back in the direction of the refrigerant compressor 12 when the stop valve A2 is open.

[0088] about Figures 6 to 9 Regarding refrigeration system 10, it should be noted that the pipeline section between the check valve R2 and the branching point Ab9 can also lead from check valve R2 to branching point Ab2. In this case, branching point Ab9 is inactive. In other words, the pipeline section after check valve R2 can be connected to the upstream or downstream of internal heat exchanger 20 on the low-pressure side.

[0089] The refrigeration device 10 with the high pressure collector 25 is particularly Figures 6 to 9 The refrigeration equipment in the system can realize selective or parallel water heat pump operation mode (through the cooler 28) and / or air heat pump operation mode (via the external heat exchanger 18) according to the selected connection mode to provide heat for the cabin supply air flow.

[0090] Further functionally, yet not further shown embodiments of the system with the possible air and water heat pump operating modes can be obtained by modifying the valve action or by supplementing valves.

[0091] An expansion device AE7 (shown in dashed lines in Figure 4 and 4A ) connected downstream of the evaporator 22 allows to adjust the intermediate pressure level in the evaporator 22, so that in addition to the heat pump operating mode, also the dehumidification function can be realized without icing of the evaporator 22, especially at low ambient temperatures.

[0092] Modifying the shut-off valve A2 arranged adjacent to the heat exchanger 18 to an expansion device AE8 (shown in dashed lines in Figure 4A , while connecting an expansion device AE9 (shown in dashed lines in Figure 4 and 4A ) downstream of the cooler 28, enables an operation in different (low) pressure levels in addition to the parallel or series operation mode of the two heat exchangers 18 and 28 in the same pressure level. Especially in the parallel operation mode, the pressure level can be adjusted by:

[0093] the pressure in the cooler 28 is greater than the pressure in the heat exchanger 18;

[0094] the pressure in the cooler 28 is less than the pressure in the heat exchanger 28;

[0095] the pressure in the cooler 28 is equal to the pressure in the heat exchanger 18.

[0096] It is generally to be noted that in all figures a plurality of sensors is shown, which are generally designated as pTX (X = 1...n). The sensors pTX are used to detect the pressure and / or the temperature of the refrigerant. It is to be noted that the number of sensors pTX (X = 1...n) or their arrangement in all figures is only shown by way of example. The refrigeration device 10 according to Figures 1 to 9 may also have more or less sensors. In the shown example, the combined pressure / temperature sensors pTX are shown as sensors. It is equally conceivable, however, to use sensors separate from one another to measure the pressure or the temperature and, if necessary, also to arrange this separate from one another in space along the refrigerant line. However, each sensor pTX explicitly mentioned in the description and / or explicitly shown in the figures can be understood as a possible relevant part of the refrigerant circuit and can be used, if necessary, especially in order to more precisely describe the structure of the refrigeration device 10 when necessary.

[0097] It is furthermore pointed out that a plurality of branching points or nodes is shown in all figures, which are denoted by AbY (Y = 1...n), without each of the plurality of branching points or nodes being explicitly described. It is pointed out that the number of branching points AbY (Y = 1...n) or their arrangement in all figures is shown only exemplarily. According to the application, more or fewer branching points can be provided. Figures 1 to 9 The refrigeration device 10 according to the application can also have more or fewer branching points. However, each branching point AbY explicitly mentioned in the description and / or explicitly shown in the figures can be understood as a possibly relevant part of the topology of the refrigerant circuit and can be used if necessary, in particular in order to more precisely describe the structure of the refrigeration device 10 if necessary.

Claims

1. A refrigeration device (10) with heat pump function for a motor vehicle, the refrigeration device having a basic system (100) implemented in a minimum configuration, the basic system comprising: Refrigerant compressor (12); a directly or indirectly acting external heat exchanger (18) arranged downstream of the refrigerant compressor; a first evaporator (22) acting directly or indirectly as part of an air conditioning device (32) for air conditioning the interior of a motor vehicle, the first evaporator being arranged downstream of an external heat exchanger (18) and the first expansion device (AE2) being connected upstream of the first evaporator; at least one second evaporator (28) as part of a cooling device for an electric drive unit or an electric storage unit, the second evaporator being arranged fluidically parallel to the first evaporator (22) and the second expansion device (AE1) being connected upstream of the second evaporator; At least one low-pressure side collector (24) arranged downstream of the first evaporator (22) and the second evaporator (28), or at least one high-pressure side collector (25) arranged downstream of the external heat exchanger (18) and upstream of the first evaporator (22) and the second evaporator (28), wherein the basic system (100) forms a main circuit (14) and can be connected to a secondary circuit (16) in terms of flow technology to realize a heat pump function, the secondary circuit branching off from the basic system (100) downstream of the refrigerant compressor (12) and having a heat source for directly or indirectly heating the air A second heat exchanger (26) is part of an air conditioning device (32), and a low-pressure side branching point (Ab2) connected to a suction section (13) is arranged downstream of a first evaporator (22), wherein refrigerant can be sucked from a main line (14) and / or a secondary line (16) via the suction section (13), the suction section being connected to the main line via a shut-off valve arranged downstream of an external heat exchanger, and a non-return valve (R1) is arranged between the first evaporator (22) and the low-pressure side branching point (Ab2), which prevents the refrigerant from flowing back into the first evaporator (22).

2. The refrigeration device (10) according to claim 1, wherein: A valve device (A3, A4) is provided downstream of the refrigerant compressor (12), and is designed to regulate the refrigerant to selectively flow to the main line (14) and / or the secondary line (16).

3. The refrigeration device (10) according to claim 1 or 2, wherein: The refrigeration device comprises an internal heat exchanger (20), a high-pressure side collector (25) being connected upstream of the internal heat exchanger on the high-pressure side, or a low-pressure side collector (24) being connected upstream of the internal heat exchanger on the low-pressure side.

4. The refrigeration device (10) according to claim 1 or 2, wherein: At least one check valve (R4) or shut-off valve (A1) is arranged and / or adjustable downstream of the second heat exchanger configured as a heating regulator and upstream of the first expansion mechanism (AE2), so that the refrigerant can selectively flow from the secondary circuit (16) to the main circuit (14) and prevent the refrigerant from flowing from the main circuit (14) to the secondary circuit (16).

5. The refrigeration device (10) according to claim 1 or 2, wherein: A check valve (R3) is arranged in the main circuit (14) downstream of the external heat exchanger (18) to prevent the refrigerant introduced from the secondary circuit (16) into the main circuit (14) from flowing back into the external heat exchanger (18).

6. The refrigeration device (10) according to claim 1 or 2, wherein: A third expansion device (AE4) is arranged in the secondary line (16) downstream of the second heat exchanger configured as a heating regulator, wherein the third expansion device (AE4) is connected upstream of the external heat exchanger (18).

7. The refrigeration device (10) according to claim 1 or 2, wherein: A bypass line having an expansion device (AE6) branches off downstream of the high-pressure side collector (25), wherein the bypass line ends between a check valve (R3) and an external heat exchanger (18), wherein the check valve (R3) is arranged between the high-pressure side collector and the external heat exchanger (18).

8. The refrigeration device (10) according to claim 1 or 2, wherein: The refrigeration device (10) is designed to operate in a reheating operating mode, in which the refrigerant flows from the refrigerant compressor (12) through the following components of the refrigeration device (10) in sequence: a second heat exchanger configured as a heating regulator in a secondary circuit, and an evaporator (22) in a primary circuit (14).

9. The refrigeration device (10) according to claim 1 or 2, wherein: The refrigeration device (10) is designed to operate in a delta process, in which the refrigerant flows from the refrigerant compressor (12) through the following components of the refrigeration device (10) in sequence: a second heat exchanger in the form of a heating regulator in the secondary circuit (16), through the second evaporator (28) in the main circuit (14) when coolant is present in a cooling device associated with the second evaporator (28).

10. The refrigeration device (10) according to claim 1 or 2, wherein: The basic system is designed as a basic module, which can be coupled and / or connected and / or integrated with at least one expansion module, which has at least a secondary circuit (16) and a second heat exchanger designed as a heating controller.

11. The refrigeration device (10) according to claim 1, wherein: The second evaporator is a cooler.

12. The refrigeration device (10) according to claim 1, wherein: The second heat exchanger is a heating regulator.

13. A motor vehicle comprising a refrigeration device (10) according to any one of claims 1 to 12.

14. The motor vehicle according to claim 13, wherein: The motor vehicle is an electrically driven motor vehicle or a partially electrically driven motor vehicle.

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