WO2023012315A1

WO2023012315A1 - Refrigerant circuit device with a plurality of inner refrigerant circuits

Info

Publication number: WO2023012315A1
Application number: PCT/EP2022/072033
Authority: WO
Inventors: Gholam Reza Zakeri
Original assignee: Sanden International (Europe) GmbH
Priority date: 2021-08-06
Filing date: 2022-08-04
Publication date: 2023-02-09
Also published as: DE102021120499A1

Abstract

The invention relates to a refrigerant circuit device (1) for a heat management system for a vehicle, which heat management system transports heat by means of at least one heat transport fluid. It comprises at least two inner refrigerant circuits (10a, 10b) which in each case have a first heat exchanger (12) and a second heat exchanger (14) for the exchange of heat between the respective refrigerant circuit. In order to make more flexible heat management and higher thermodynamic efficiency for the heat management in vehicles possible, the refrigerant circuit device (1) has a first switchover device (20) which is connected to the first heat exchangers (12) with a first fluid connector (21) and a second fluid connector (22) for conducting heat transport fluid through the first heat exchangers (12), which first switchover device (20) is configured to switch the first heat exchangers (12) selectively in series sequentially or parallel to one another between the first fluid connector (21) and the second fluid connector (22).

Description

Refrigerant cycle device having multiple internal refrigerant circuits

The invention relates to a refrigerant circuit device for a heat management system for a vehicle, the heat management system transporting heat by means of at least one heat transport fluid. The invention also relates to a heat management system for a vehicle with such a refrigerant circuit device.

In its basic form as an air conditioning system, a heat management system for a vehicle comprises a refrigerant circuit with a compressor, an expansion valve, a first heat exchanger and a second heat exchanger. A refrigerant circulates through the refrigerant circuit. The thermal management system can be operated, for example, in a cooling mode such that heat is removed from a vehicle interior by means of the second heat exchanger and heat is released to an (external) environment by means of the first heat exchanger. This cools the vehicle interior. Conversely, the thermal management system can be operated in a heating mode such that heat is absorbed from the external environment by means of the first heat exchanger and heat is released into the vehicle interior by means of the second heat exchanger. This heats the vehicle interior.

The air conditioning system can be designed as a direct, indirect or combined air conditioning system.

US 2013/0152611 A1 first shows a direct air conditioning system for a vehicle with a compressor, an interior condenser, an interior heat exchanger, an exterior heat exchanger and expansion valves. The inner heat exchanger can be an evaporator, for example, and the outer heat exchanger can be a condenser, gas cooler or evaporator, for example

be. In this direct air conditioning system, a direct heat exchange between the refrigerant and the air for the vehicle interior takes place by means of the internal heat exchanger. A direct heat exchange between the refrigerant and the ambient air (outside air) also takes place by means of the external heat exchanger. The targeted transfer of heat between the heat sink and the heat source is therefore carried out exclusively by means of the refrigerant. In a modification, an additional heat exchanger enables the exchange of heat with an additional fluid circuit comprising an additional heat source or heat sink, for example a radiator of an electric motor or a battery of the vehicle. The fluid of the second fluid circuit is water, for example. This modification thus shows a combined air conditioning system in which the additional heat source or heat sink does not exchange heat directly with the refrigerant, but indirectly via the water of the additional fluid circuit.

EP 3 118 035 A1 describes a temperature adjustment device for an electric vehicle. It is an indirect system with a refrigerant circuit, a low-temperature water circuit and a high-temperature water circuit.

US 2008/0196877 A1 describes a heating, ventilation and air conditioning system for heating and cooling a passenger compartment of a vehicle. In a primary circuit, a compressor compresses high-pressure refrigerant. Heat is exchanged between the primary circuit and a secondary circuit via a heat exchanger. The secondary circuit is a low-pressure liquid circuit.

Refrigerant systems for vehicles are usually designed in such a way that they cover very high to very low power requirements.

All of the above solutions use a single, central refrigerant circuit to cover different cooling and heating requirements under different operating conditions or even operating modes. In order to also be able to meet high performance requirements, the refrigerant circuit must be designed with correspondingly high performance. For example, in an electric vehicle, a very high cooling capacity is required during a rapid charging process of a vehicle battery at a rapid charging station, since a large amount of heat has to be removed in a short time during the rapid charging process. This aspect must be taken into account when designing all components of the refrigerant system.

During operation, the maximum capacity of the refrigerant circuit is typically only rarely required. The refrigerant circuit is mainly operated in the partial load range. In the partial load range, however, the efficiency is not optimal. This leads to increased energy consumption in the partial load range compared to the hypothetical case that the refrigerant circuit would be specifically designed for the corresponding performance. In electric vehicles, the increased energy consumption of the refrigerant circuit leads to lower overall efficiency and range.

In addition, the compressor of the central refrigeration system must always work against the total temperature difference (a difference between the temperatures of the heat sink and the heat source).

DE 10 2011 015 151 A1 describes a heat pump cycle that is typically used for a vehicle air conditioning system of a hybrid vehicle. An electrically driven compressor of a two-stage boost type is used. It has a first compression mechanism and a second compression mechanism which are connected in series in immediate succession. When the vehicle air conditioner is in a heat pump mode for heating

zen, a refrigerant heated by a water-refrigerant heat exchanger flows into a medium-pressure port of the two-stage compressor. The intermediate pressure port is located between the first compression mechanism and the second compression mechanism. By setting a pressure of an intermediate-pressure refrigerant to a value close to the square root of the product of a pressure of the high-pressure refrigerant and a pressure of the low-pressure refrigerant, a high coefficient of performance (abbreviated "COP" for English. "Coefficient of performance") is achieved. In a cooling mode, fluid flows into the compressor through a suction port located upstream of the first compression mechanism, but not through the intermediate pressure port.

The object of the present invention is to enable more flexible heat management and higher thermodynamic efficiency for heat management in vehicles.

The above object is achieved by a refrigerant cycle device having the features of claim 1 .

The refrigerant cycle device is suitable for a thermal management system for a vehicle, wherein the thermal management system transports heat by means of at least one (first) heat transport fluid.

The refrigerant circuit device has at least two self-contained, internal refrigerant circuits, the refrigerant circuits each

- A first heat exchanger for exchanging heat between the respective refrigerant circuit and (the first) heat transport fluid and

- A second heat exchanger for exchanging heat between the respective refrigerant circuit and (the first heat transport fluid or a second) heat transport fluid

comprise and are arranged to pump heat between the second heat exchanger and the first heat exchanger.

The refrigerant cycle device also includes a first (heat transport fluid) switching device connected to the first heat exchanger and having a first fluid connection and a second fluid connection for conducting (the first) heat transport fluid through the first heat exchanger.

The first switching device is set up to switch the first heat exchangers of the at least two refrigerant circuits either in series one behind the other or in parallel to one another between the first fluid connection and the second fluid connection.

The refrigerant circuit device allows the at least two refrigerant circuits to be switched differently depending on the required power, the operating conditions and/or the operating modes or to allow heat transport fluid to flow through them. This enables a particularly high level of efficiency for different performance requirements, operating conditions and operating modes. The refrigeration cycle device allows for more flexible thermal management and higher thermodynamic efficiency. The operating conditions can be, for example, a temperature and humidity of the environment, a temperature and humidity in a vehicle interior, a temperature gradient between the vehicle interior and the environment, heat input into the vehicle interior (e.g. due to solar radiation and/or vehicle occupants), waste heat from the vehicle (e.g. by a battery, electronics and/or an internal combustion engine of the vehicle).

As described above, the respective refrigerant circuits for pumping heat between the (respective) second heat exchanger and the (respective)

set up the first heat exchanger. This can mean the respective refrigerant circuits are

- Set up for pumping heat from the second heat exchanger to the first heat exchanger or

- Set up for pumping heat from the first heat exchanger to the second heat exchanger or

- Set up (switchable) for pumping heat either from the second heat exchanger to the first heat exchanger or from the first heat exchanger to the second heat exchanger.

In the following it can be assumed without loss of generality that the refrigerant circuits are set up (at least) for pumping heat from the second heat exchanger to the first heat exchanger.

The individual internal refrigerant circuits are self-contained. As a result, the individual refrigerant circuits have a simple structure, are robust and reliable. The refrigerant circuits remain compact. As a result, the flow resistances in the individual refrigerant circuits are small. Many refrigerants are difficult to produce, expensive, difficult to dispose of, harmful to the environment and/or flammable. Since the individual refrigerant circuits are closed, only a minimal amount of each refrigerant is required. In addition, refrigerant circuits typically have to be able to withstand high internal pressures caused by the refrigerant. Refrigerant circuits have to be built in a correspondingly complex, solid and heavy manner. Since the individual refrigerant circuits are closed here, the cost of materials, installation space and weight remain manageable.

Especially when using the refrigerant circuit device in a vehicle, such as a car or a truck, ensure the

mentioned advantages for further, secondary positive effects, for example for reduced energy or fuel consumption when driving, a higher power-to-weight ratio and better driving performance. Consequently, the refrigerant circuit device is particularly efficient and environmentally friendly. In addition, the structure with individual, closed internal refrigerant circuits simplifies maintenance. All other parts of the thermal management system can be serviced, repaired and/or replaced without having to drain the refrigerants in the refrigerant circuits. Even if one of the refrigerant circuits itself requires maintenance or repair, only the refrigerant from the affected refrigerant circuit needs to be drained.

In addition, the present invention facilitates the miniaturization of the refrigeration cycle device itself, and particularly of more complex thermal management systems. The individual refrigerant circuits and their element can be very small, light and efficient. The modular design enables simple, precise and cost-effective adaptation to a wide variety of conditions.

The respective refrigerant circuits can be designed, for example, as a compression heat pump, as an absorption heat pump, as an adsorption heat pump, as an electrocaloric heat pump or as a magnetocaloric heat pump. The individual refrigerant circuits can generally be designed differently from one another.

Each of the refrigerant circuits preferably has (at least) one circulation device for circulating the refrigerant in this refrigerant circuit. The circulating device may, for example, comprise a compressor (in the case of a compression heat pump), a pump and/or a heated evaporator (absorption system).

According to a further aspect, each of the refrigerant circuits has at least one expansion valve. Different refrigerant circuits can generally have different expansion valves. The respective expansion valve can be uncontrolled or controlled. The respective expansion valve can, for example, comprise a capillary tube and/or a thermostatic expansion valve. The thermostatic expansion valve can be designed in particular as a block valve.

Particularly preferably, the refrigerant circuits each include

- A compressor for the circulation of the respective refrigerant of the refrigerant circuit and

- an expansion valve.

The refrigerant circuits are each designed as compression heat pumps. Compression heat pumps are reliable and allow high performance, especially in relation to their dimensions and weight. They are therefore particularly suitable for use in vehicles.

In the respective refrigerant circuit, the first heat exchanger is set up to exchange heat between the refrigerant of this refrigerant circuit and heat transport fluid that is routed through the first switching device. In particular, the first heat exchanger can be set up to absorb heat from the heat transport fluid routed through the first switching device into the respective refrigerant and/or to release heat from the respective refrigerant into the heat transport fluid routed through the first switching device.

According to a further aspect, the refrigerant circuits are closed off from one another and independent of one another. Even if one of the refrigerant circuit

fails, the remaining refrigerant circuit or the remaining refrigerant circuits can continue to be operated. If the vehicle is on the move (e.g. on a road), safe (emergency) operation is guaranteed until it reaches a garage or workshop.

The refrigerant circuits can generally be viewed as a "black box". The internal structure of the refrigerant circuits can differ from each other. One, several or all refrigerant circuits can have additional components.

In a preferred embodiment of the invention, at least one of the refrigerant circuits has an additional internal heat exchanger. A "warm side" of the indoor heat exchanger can be integrated into the refrigerant circuit along a flow direction of the refrigerant between the first heat exchanger and the expansion valve. A "cold side" of the indoor heat exchanger may be connected to the refrigerant cycle along the flow direction of the refrigerant between the second heat exchanger and the inlet of the circulating device (e.g., a suction of the compressor). The indoor heat exchanger may be configured to enable an exchange of heat between the refrigerant that flows out of the first heat exchanger and the refrigerant of the same refrigerant circuit that is sucked into the compressor. The refrigerant emerging from the first heat exchanger is (further) supercooled by means of the interior heat exchanger. In return, the refrigerant exiting the second heat exchanger and being sucked into the compressor is additionally overheated. The indoor heat exchanger enables higher efficiency. In particular, an internal heat exchanger can be provided in each of several or all refrigerant circuits.

Alternatively, at least one of the refrigerant circuits can have an accumulator for refrigerant. In particular, several or all of the refrigerant circuits can each have an accumulator for refrigerant.

In an advantageous embodiment of the invention, the first switching device is set up for connection to a first heat transport fluid circuit of the heat management system. In particular, the first switching device can be set up to form an “inner part” of the first heat transfer fluid circuit when it is connected to a remaining (outer) part of the heat transfer fluid circuit. As a result, the refrigerant circuit device can be easily integrated into the heat management system. The first heat exchangers of the (at least two) refrigerant circuits in the heat transport fluid circuit can be switched in series (one behind the other along a heat transport fluid flow direction) or parallel to one another as required using the first switching device.

The refrigerant circuit device is preferably set up in such a way that the first switching device has a switchable direct fluid connection for (the first) heat transport fluid between two consecutive ones of the at least two refrigerant circuits, with this switchable direct fluid connection for the heat transport fluid between the first heat exchangers of the two consecutive refrigerant circuits

- is manufactured in its series connection state and

- is interrupted in its parallel connection state and instead

• establishes a direct fluid connection for (the first) heat transport fluid between the first heat exchanger of one of the two consecutive refrigerant circuits and the second fluid connection, which interrupts it in its series connection state, and

• establishes a direct fluid connection for the heat transport fluid between the first heat exchanger of the other of the two successive refrigerant circuits and the first fluid connection, which interrupts them in their series connection state.

The respective first heat exchangers of the respective consecutive refrigerant circuits are therefore connected consecutively in series in the series connection state along the direction of flow of the heat transport fluid.

Two consecutive refrigerant circuits are two spatially adjacent refrigerant circuits, for example refrigerant circuits positioned close to one another or adjacent to one another.

The implementation of the (at least one) switchable direct fluid connection between the first heat exchangers of the successive refrigerant circuits enables the first switching device to be implemented in a structurally simple, cost-effective, light and reliable manner.

The at least one switchable direct fluid connection (extremely preferably each switchable fluid connection) between the first heat exchangers of two successive refrigerant circuits particularly preferably has a first device for flow diversion and a second device for flow diversion, with the first device for flow diversion and the second device for flow diversion at least enable the first heat exchanger of the successive refrigerant circuits to be switched either in parallel or in series between the first fluid connection and the second fluid connection.

In one development, the first device and second device for flow diversion are also set up to direct a first partial flow of the heat transport fluid between the first fluid connection and the second fluid connection only through the first heat exchanger of one of the two successive refrigerant circuits, and a second partial flow of the heat transport fluid only to pass through the first heat exchanger of the other of the two successive refrigerant circuits and to pass a third partial flow of the heat transport fluid through both said first heat exchangers in succession. In a development, the ratio between the first partial flow, the second partial flow and the third partial flow can be adjusted, extremely preferably adjusted as desired.

The at least one switchable direct fluid connection (very preferably each switchable fluid connection) between the first heat exchangers of two successive refrigerant circuits particularly preferably has a first three-way valve and a second three-way valve, with the respective first three-way valve is in direct fluid communication with

- the first heat exchanger of one of the two consecutive refrigerant circuits, for example via an AB connection of this first three-way valve,

- The respective second three-way valve, for example via a B connection of this first three-way valve, and

- The second fluid connection, for example via an A-connection of this first three-way valve, the respective second three-way valve being in direct fluid connection with

- the first heat exchanger of the other of the two adjacent refrigerant circuits, for example via an AB connection of this second three-way valve,

- The respective first three-way valve, for example via a B connection of this second three-way valve, and

- The first fluid connection, for example via an A-connection of this second three-way valve.

In this way, the first switching device can be implemented with inexpensive, small, light, reliable and readily available components. The respective first three-way valve and the respective second three-way valve are extremely preferably designed as changeover valves, for example as 3/2-way changeover valves, or as mixing valves, in particular as controllable mixing valves.

In another embodiment, the at least one switchable direct fluid connection (extremely preferably each switchable direct fluid connection) between the first heat exchangers of two successive refrigerant circuits particularly preferably has a four-way valve in each case. The four-way valve can, for example, in a first valve position, connect a heat transport fluid outlet of one of these two first heat exchangers to a heat transport fluid inlet of the other of these two first heat exchangers and in a second valve position said heat transport fluid outlet to the second fluid passage connect and connect said heat transfer fluid inlet to the first fluid passage. The four-way valve can be limited to the first valve position and the valve position position (4/2-way valve). This makes it simple, robust and inexpensive. Optionally, the four-way valve can have at least one additional valve position. This provides greater flexibility. For example, this can make it possible to block one or both of the two successive refrigerant circuits.

Here, without restricting the generality, it is assumed that the first heat transport fluid in the first switching device has a flow direction from the first fluid connection (inlet) to the second fluid connection (outlet). In particular, the designations are heat transport fluid inlet and

Against this background, heat transport fluid outlet of the first heat exchanger is not to be understood as limiting. In general, it is alternatively or additionally possible for (the first) heat transport fluid to flow in the opposite direction of flow within the first switching device through the first switching device and thus the first heat exchanger, ie from the second fluid connection to the first fluid connection.

In a further development of the invention, the first heat exchanger of a first of the at least two refrigerant circuits is in direct fluid connection with the first fluid connection, independently of the switching states of the first switching device, and the first heat exchanger of a last of the at least two refrigerant circuits is in direct fluid connection, independently of the switching states of the first switching device direct fluid communication with the second fluid port.

This enables a compact, inexpensive, light, robust, simple and reliable structure with few components.

In an advantageous embodiment, the refrigerant circuit device comprises a second (heat transport fluid) switchover device connected to the second heat exchanger and having a third fluid connection and a fourth fluid connection for conducting heat transport fluid through the second heat exchanger, the second switchover device being set up to switch the second heat exchanger of the switch at least two refrigerant circuits either in series or parallel to each other between the third fluid port and the fourth fluid port.

All of the described embodiments, modifications and advantages that relate to the first switching device can be used analogously as an alternative or in addition to the second switching device.

In the respective refrigerant circuit, the second heat exchanger is set up to exchange heat between the respective refrigerant of this refrigerant circuit and heat transport fluid that is routed through the second switching device. In particular, the second heat exchanger can be set up to absorb heat from the heat transport fluid routed through the second switching device into the respective refrigerant and/or to release heat from the respective refrigerant into the heat transport fluid routed through the second switching device.

According to a further aspect, the second switching device is set up for connection to the first heat transport fluid circuit and/or to a second heat transport fluid circuit of the heat management system. In particular, the second switching device can be set up to form part of the first heat transfer fluid circuit when connected to the remaining (outer) part of the first heat transfer fluid circuit and/or to form part of the second heat transfer fluid circuit , when connected to a remaining (outer) part of the second heat transfer fluid circuit. As a result, the refrigerant circuit device can be easily integrated into the heat management system. The second heat exchanger of the (at least two) refrigerant circuits in the first or second heat transport fluid circuit can be switched in series or parallel to one another as required by means of the second switching device.

According to a further aspect, the at least two refrigerant circuits can be operated independently of one another. As a result, the power provided by the refrigerant circuit device can be flexibly adjusted. In particular, the circulation devices of the at least two refrigerant circuits can be operated independently of one another. It is conceivable, for example, only one of the circulation devices and thus only one of the refrigerant circuits

to operate at all when only little power is required by the refrigerant circuit device. Since at this point in time this one circulation device alone provides the currently required power, the corresponding refrigerant circuit can nevertheless be operated in an advantageous load range. In particular, the efficiency is higher than if, in the same situation, the circulating devices of all refrigerant circuits were operated simultaneously and each at very low power.

As an alternative or in addition, the refrigerant circuit device is preferably set up to operate one of the at least two refrigerant circuits with a stationary output and to operate another of the at least two refrigerant circuits with an output that is tailored to the needs. In vehicles, a certain (at least essentially) constant basic power must often be provided by the refrigerant circuit device for a large part of the time, for example for cooling the vehicle interior. This basic power is provided by the circulating device operated with stationary power. However, in other situations, the refrigerant cycle device must provide a much higher performance, for example during the quick charging of a vehicle battery of an electric vehicle, wherein heat is removed from the vehicle battery by means of heat transport fluid. The at least one further refrigerant circuit is then switched on automatically as required. In particular, the refrigerant circuit device can be set up to operate the circulation device of one of the at least two refrigerant circuits with a stationary output and to operate the circulation device of the other of the at least two refrigerant circuits with a demand-based output.

In a particularly advantageous embodiment of the invention, the compressor of at least one of the refrigerant circuits has a fixed cubic capacity. This makes the compressor cost-effective and particularly light.

As an alternative or in addition, the compressor of at least one other of the refrigerant circuits has a variable cubic capacity and/or speed control to adjust the output during operation.

R1234yf, R744 (CO2), R436b, R290 and/or R1234ze(E), for example, can be used as refrigerants in the refrigerant circuits.

Preferably, one of the at least two refrigerant circuits includes a first refrigerant and a second of the refrigerant circuits includes a second refrigerant, which differs from the first refrigerant. The different refrigerant circuits can thus be designed for different operating conditions, operating modes and/or requirements. This allows the refrigerant circuit device to be operated very efficiently under different operating conditions, operating modes and/or requirements. Depending on the operating conditions, operating modes and/or requirements, different refrigerants can enable different efficiencies. The refrigerant circuit with the most suitable refrigerant can be used alone or at full power, while the other refrigerant circuit or the other refrigerant circuits are not operated or are operated with as little power as possible.

In an advantageous embodiment, the refrigerant circuit device has at least three self-contained, internal refrigerant circuits, with the first switching device being set up to switch the first heat exchangers of two consecutive ones of the at least three refrigerant circuits either in series one behind the other or parallel to one another between the first fluid connection and the second fluid connection to switch.

If the refrigerant cycle device includes three (inner) refrigerant circuits, the first switching device allows, for example,

- To switch the first heat exchanger of a first and a second of the refrigerant circuits in the heat transport fluid circuit either in series or in parallel with one another and

- Switch the first heat exchanger of the second and a third of the refrigerant circuits in the heat transport fluid circuit either in series or in parallel with one another.

In this example there are therefore two switchable direct fluid connections in the previously mentioned sense. As a result, the first switching device makes it possible, among other things, to switch the first heat exchangers of the first, the second and the third refrigerant circuit either in series or in parallel with one another. A total of four different switching states of the first switching device are possible.

Alternatively or additionally, in one development of the invention, the second switching device is set up to switch the second heat exchangers of two consecutive ones of the at least three refrigerant circuits either in series one behind the other or parallel to one another between the third fluid connection and the fourth fluid connection.

The structure of the refrigerant circuit device with several self-contained internal refrigerant circuits enables a high degree of modularity and scalability. A number of the refrigerant circuits can be implemented depending on performance requirements, operating modes and/or operating conditions. For example, one or more additional refrigerant circuits can be added in a simple manner in order to provide high maximum performance. Nevertheless, good efficiency is ensured. The load distribution between the refrigerant circuits can be changed. For example, one of the refrigerant circuits can be switched off completely if the remaining refrigerant

Circuit or the other refrigerant circuits can provide the power currently required. As a result, the refrigerant circuit device can also ensure high efficiency for a wide variety of performance requirements, operating modes and operating conditions.

The structure with several internal refrigerant circuits is particularly advantageous when very different temperature levels occur during operation. This is the case, for example, when the thermal management system is set up to manage the temperature of the vehicle battery on the one hand and to cool the vehicle interior on the other. The optimum operating range for vehicle batteries is typically in the range of 30°C to 35°C, whereas the temperature required to cool the vehicle interior can be as low as 3°C or above 3°C, for example in the range of 3°C to 15°C . If the focus is on controlling the temperature of the vehicle battery, the heat transport fluid flowing out of the refrigerant device and conducted to the vehicle battery should ideally have a higher, first temperature. On the other hand, if the priority is to cool the vehicle interior, the heat transfer fluid exiting the refrigeration device and routed to an HVAC unit should ideally have a lower, second temperature. Depending on the temperatures of the heat transport fluid in the refrigerant circuit device, it can be more efficient, for example, to use a first part of the refrigerant circuits or to use a second part of the refrigerant circuits.

In an extremely preferred embodiment, the refrigerant circuit device is set up to optionally allow the first heat transport fluid to flow through the first heat exchangers (e.g. the heat sink side of the refrigerant device) in parallel and the first heat exchangers (e.g. the heat source side of the refrigerant device) in series to let the second heat transport fluid flow through and / or optionally

allowing the first heat transfer fluid to flow through the second heat exchanger in series and allowing the second heat transfer fluid to flow through the first heat exchangers in parallel.

The use of the multiple refrigerant circuits and the possibility of connecting the first heat exchangers in series or in parallel and/or the second heat exchangers in series or in parallel makes it possible to ensure efficient operation even for different requirements and operating modes. For example, the first heat transport fluid can flow through the first heat exchanger (on the heat sink side of the refrigerant device) either in series (in series) or in parallel one behind the other. In the case of parallel flow, the parallel partial flows of the first heat transport fluid mix through the different first heat exchangers when they combine downstream of the first heat exchangers.

In one development, the first switching device also makes it possible to optionally not switch individual first heat exchangers between the first fluid connection and the second fluid connection (switched off individually).

The above object is also achieved by a thermal management system for a vehicle having the features of claim 10.

The heat management system is set up to form (at least) a first heat transport fluid circuit. It also includes the refrigerant circuit device according to any one of the described embodiments, wherein the first switching device is integrated into the first heat transport fluid circuit.

The features, embodiments, modifications and advantages described with reference to the refrigerant circuit device apply accordingly to the thermal management system and vice versa, the features, embodiments, modifications and advantages described with reference to the thermal management system apply accordingly to the refrigerant circuit device, its operation and/or its use.

In particular, the first switching device is connected to an outer part of the first heat transport fluid circuit via the first fluid connection and the second fluid connection. The first switching device and the first heat exchanger form an inner part of the first heat transport fluid circuit.

The heat management system is preferably set up to (simultaneously) form a first heat transport fluid circuit and a second heat transport fluid circuit. It further comprises the refrigerant cycle device having the first switching device and a second switching device according to any of the respective described embodiments, wherein the first switching device is connected to the first heat-transporting fluid circuit and the second switching device is connected to the second heat-transporting fluid circuit.

In particular, the second switching device is connected to an outer part of the second heat transport fluid circuit via the third fluid connection and the fourth fluid connection. The second switching device and the second heat exchangers form an inner part of the second heat transport fluid circuit.

In an advantageous embodiment, the thermal management system includes at least one heat sink. The heat management system can emit heat via the heat sink, for example to the vehicle interior (interior of the vehicle) and/or to the environment. Particularly preferably, the first heat transfer fluid circuit comprises the heat sink or the heat sink can be switched (integrated) into the first heat transfer fluid circuit.

In an extremely preferred development, the heat management system comprises a number of heat sinks and is set up for a number of operating modes, with the heat sinks being switched (integrated) individually differently into the first heat transport fluid circuit or not depending on the operating mode. For the purpose of this disclosure, "plural" means "at least two".

According to another aspect, the thermal management system includes at least one heat source. The heat management system can absorb heat via the heat source, for example from the air for the vehicle interior and/or from the environment. The second heat transport fluid circuit particularly preferably comprises the heat source or the heat source can be switched (integrated) into the second heat transport fluid circuit.

In an extremely preferred development, the heat management system comprises a number of heat sources and is set up for a number of operating modes, with the heat sources depending on the operating mode being switched (integrated) individually differently into the second heat transport fluid circuit or not.

According to a further aspect, the refrigerant circuit device is particularly preferably set up to extract heat from the second heat transport fluid circuit

to pump in the first heat transfer fluid circuit. The first heat transport fluid circuit represents a heat sink and the second heat transport fluid circuit represents a heat source for the refrigerant circuit device.

The heat transfer fluid of the first heat transfer fluid circuit and the heat transfer fluid of the second heat transfer fluid circuit can be different. The first heat transfer fluid circuit and the second heat transfer fluid circuit preferably have the same heat transfer fluid. The heat transfer fluid can include water and/or glycol, for example. In particular, the heat transport fluid can consist of at least 90% by mass of water and/or glycol. For example, the heat transfer fluid may be (at least substantially) 50% water and 50% glycol by mass, or 50% water and 50% glycol by volume.

The thermal management preferably has an HVAC unit. The HVAC unit may have two heat exchangers. In particular, the HVAC unit may include an HVAC heat absorber and an HVAC radiator. "HVAC" is the abbreviation for the English term "heating, ventilation, and air conditioning system".

The HVAC heat absorber may be configured for cooling an interior of the vehicle (a vehicle interior), for example by air directed into the vehicle interior flowing through the HVAC heat absorber, thereby releasing heat to the thermal management system, for example the heat transfer fluid of the first Heat transfer fluid circuit or the second heat transfer fluid circuit. The thermal management system is configured to use the HVAC heat absorber as a heat source for the thermal management system. For example, the heat management

ment system can be configured such that the HVAC heat absorber can be integrated or is integrated as a heat source in at least one of the first heat transport fluid circuit and the second heat transport fluid circuit, in particular in the second heat transport fluid circuit. In other words, heat is released from the air for the vehicle interior and this heat is transported away by the heat management system. For example, this heat can ultimately be given off to the surroundings of the vehicle.

The HVAC radiator may be configured to heat the interior of the vehicle (vehicle cabin), for example by air blown into the vehicle cabin flowing through the HVAC radiator while absorbing heat from the thermal management system, for example the heat transfer fluid of the first heat transfer fluid -Circle or the second heat transport fluid circuit. The thermal management system is set up so that the HVAC radiator can be used as a heat sink for the thermal management system. For example, the thermal management system can be configured such that the HVAC radiator can be or is integrated into at least one of the first heat transport fluid circuit and the second heat transport fluid circuit as a heat sink, in particular into the first heat transport fluid circuit.

In a development of the invention, the heat management system is additionally set up to integrate both the HVAC heat absorber and the HVAC radiator into the first heat transport fluid circuit at the same time, for example in a maximum heating mode. As a result, both can be used simultaneously to release heat to the air for the vehicle interior. This enables a very high heating output. In addition, the HVAC unit can be made more compact and lighter without sacrificing maximum heat transfer for heating.

In particular, the HVAC unit with the HVAC heat absorber and an HVAC radiator can have an HVAC switching device which is designed to selectively integrate the HVAC heat absorber into the second heat transport fluid circuit or into the first heat together with the HVAC radiator - to include the metransportfluid circuit.

Alternatively or additionally, the heat management system is preferably set up to include both the HVAC heat absorber and the HVAC radiator in the second heat transport fluid circuit at the same time, for example in a maximum cooling mode. As a result, both can be used simultaneously to absorb heat from the air for the vehicle interior. This enables a very high cooling capacity. In addition, the HVAC unit can be made more compact and lighter without sacrificing maximum heat transfer for cooling.

In particular, the HVAC switching device can be set up to optionally integrate the HVAC radiator into the first heat transport fluid circuit or to integrate it together with the HVAC heat absorber into the second heat transport fluid circuit.

In general, the HVAC heat absorber can also be referred to as the first HVAC heat exchanger. Correspondingly, the HVAC radiator can also be generally referred to as a second HVAC heat exchanger. The more memorable terms HVAC heat absorber and HVAC radiator will be used throughout this disclosure solely for ease of legibility and distinguishability.

In another aspect, the thermal management system preferably includes an interior fan for injecting air into the vehicle interior, the inducted air flowing through the HVAC unit. The blown

Air can, for example, have been taken from the environment and/or the vehicle interior (air recirculation mode).

Alternatively or additionally, the thermal management system has at least one external heat exchanger for exchanging heat with the environment. The external heat exchanger can be designed as a radiator, for example. The heat management system can be set up so that heat transport fluid flows through the external heat exchanger in order to exchange heat with the environment. Depending on the operating mode, the outdoor heat exchanger can serve as a heat source (e.g. in heating mode) or as a heat sink (e.g. in cooling mode).

In an advantageous embodiment, the heat management system is set up to use at least one of the following waste heat sources of the vehicle as a heat source in at least one operating mode:

- an electric motor to drive the vehicle,

- a battery to supply the electric motor with electricity,

- A power electronics of the vehicle and / or

- an internal combustion engine of the vehicle.

In particular, the heat management system can be set up to integrate the at least one waste heat source into the second heat transport fluid circuit as a heat source, depending on the operating module.

Alternatively or additionally, the heat management system is preferably set up to supply heat to at least one of the following components of the vehicle as a heat sink in at least one operating mode:

- the vehicle battery to supply the electric motor with electricity,

- the power electronics of the vehicle and/or

- an internal combustion engine of the vehicle.

In particular, the heat management system can be set up to integrate the at least one component into the first heat transport fluid circuit as a heat sink depending on the operating mode.

When the temperature is low, the performance of the vehicle battery is reduced. The efficiency of the power electronics can also be reduced at low temperatures. Warming up the temperature of the combustion engine to its operating temperature more quickly during the starting phase reduces emissions, increases efficiency, improves environmental friendliness and protects the combustion engine. In particular, the heat management system can be set up to integrate the at least one waste heat source as a heat source in the second heat transport fluid circuit.

The thermal management system is an indirect thermal management system. The individual internal refrigerant circuits are completed. They are not in fluid communication with the "outside" heat transfer fluids. The above benefits apply accordingly.

The above object is also achieved by using a refrigerant cycle device or a thermal management device according to any one of the described embodiments in a vehicle.

The above object is also achieved by a vehicle having a refrigerant circuit device or a heat management device according to any one of the described embodiments.

A vehicle within the meaning of this application preferably means a motor vehicle, such as passenger cars, trucks and buses. It is particularly preferably an electric vehicle or a hybrid vehicle, for example an electrically powered passenger car or a

Passenger cars with hybrid drive. A hybrid vehicle has a combination of an internal combustion engine with at least one electric motor for the traction drive.

The invention is explained below using exemplary embodiments and with reference to the figures. All of the features described and/or illustrated form the subject matter of the invention, either alone or in any combination, even independently of their summary in the claims or their back-references

They show schematically:

1 shows the structure of a first embodiment of a refrigerant circuit device according to the invention with two independent internal refrigerant circuits, a first switching device for first heat transfer fluid heat exchangers of the refrigerant circuits and a second switching device for second heat transfer fluid heat exchangers of the refrigerant circuits;

Fig. 2 shows the refrigerant cycle device from Fig. 1 in a state in which the first switching device switches the first heat exchangers in series between a first fluid connection and a second fluid connection for a first heat transport fluid of a heat management system and in which the second switching device switches the second heat exchangers in series between switches a third fluid port and a fourth fluid port for a second heat transport fluid of the thermal management system;

FIG. 3 shows the refrigerant circuit device from FIG. 1 in a state in which the first switching device connects the first heat exchangers in parallel

mutually switches between the first fluid port and the second fluid port and in which the second switching device switches the second heat exchangers in parallel between the third fluid port and the fourth fluid port;

4 shows the structure of a second embodiment of a refrigerant circuit device according to the invention with three internal refrigerant circuits that are independent of one another;

5 shows the structure of a third embodiment of a refrigerant circuit device according to the invention with four internal refrigerant circuits that are independent of one another;

FIG. 6 shows a first embodiment of a thermal management system according to the invention for a passenger car with an electric drive with the refrigerant circuit device from FIG. 1 with additional pumps in a cooling mode;

FIG. 7 shows the thermal management system from FIG. 6 in a heat pump mode or heating mode using ambient air, a vehicle battery and power electronics of the vehicle as heat sources;

FIG. 8 shows the thermal management system from FIG. 6 in an internal source heating mode using the vehicle battery and the power electronics of the vehicle as heat sources;

FIG. 9 shows the thermal management system of FIG. 6 in a reheat mode;

FIG. 10 shows the thermal management system from FIG. 6 in a pure external cooling mode for cooling the vehicle battery and the electronics; and

11 shows a second embodiment of a heat management system according to the invention for a passenger car with an electric drive, with the refrigerant circuit device from FIG to switch a second heat transport fluid circuit.

Fig. 1 shows a first embodiment of a refrigerant circuit device 1 according to the invention with two independent inner refrigerant circuits 10a, 10b. Each of the refrigerant circuits 10a, 10b has a compressor 11 for compressing the refrigerant of the respective refrigerant circuit 10a, 10b, a first heat exchanger 12, an expansion valve 13 and a second heat exchanger 14.

The refrigerant circuit device 1 also has a first switching device 20 for heat transport fluid and a second switching device 40 for heat transport fluid.

The refrigerant circuit device 1 can be integrated into a heat management system for a vehicle, as described below by way of example with reference to FIGS. 6 to 11 with reference to heat management systems 300, 400.

The first switching device 20 is connected to all first heat exchangers 12 and is used to conduct heat transfer fluid, for example a first heat transfer fluid of the heat management system 300, through the first heat exchanger 12. It has a first fluid connection 21 and a

second fluid port 22 on. Heat transport fluid, for example the first heat transport fluid, can flow through the first switching device 20 and the first heat exchanger 12 via the first fluid connection 21 and the second fluid connection 22 . The first heat exchangers 12 each enable the exchange of heat between (the first) heat transport fluid and the refrigerant of the respective refrigerant circuit 10a, 10b.

In the heat management system 300 shown in Fig. 6, the first fluid connection 21 is used to introduce the first heat transport fluid into the first switching device 20 and the second fluid connection 22 is used to outlet the first heat transport fluid from the first switching device 20. The first switching device 20 is shown in Fig. 6 9 together with the first heat exchangers 12 each an ("inner") part of a heat sink-side, first heat transport fluid circuit 301 of the heat management system 300. The first heat transport fluid circulates in the first heat transport fluid circuit 301.

The second switching device 40 is connected to all second heat exchangers 14 and is used to conduct heat transport fluid, for example a second heat transport fluid of the heat management system 300, through the second heat exchanger 14. It has a third fluid connection 41 and a fourth fluid connection 42. Heat transport fluid, for example the second heat transport fluid, can flow through the second switching device 40 and the second heat exchanger 14 via the third fluid connection 41 and the fourth fluid connection 42 . The second heat exchanger 14 enable the exchange of heat between (the second) heat transport fluid and the refrigerant of the respective refrigerant circuit 10a, 10b.

In the heat management system 300 shown in FIG. 6, the third fluid connection 41 is used to introduce the second heat transport fluid into the second switching device 40 and the fourth fluid connection 42 is used to outlet the

second heat transport fluid from the second switching device 40. The second switching device 40 in Fig. 6 to Fig. 9 together with the second heat exchangers each form an ("inner") part of a heat source-side, second heat transport fluid circuit 310 of the heat management system 300. The second heat transport fluid circulates in the second heat transfer fluid circuit 310.

The linguistic distinction between the first heat transport fluid and the second heat transport fluid serves to simplify the description and does not exclude the first heat transport fluid and the second heat transport fluid being of identical composition. The first heat transfer fluid and the second heat transfer fluid may generally have the same composition or different compositions. In the illustrated embodiment, the first heat transfer fluid and the second heat transfer fluid preferably have the same composition. For example, they can consist at least essentially (at least 95% by mass) of a water-glycol mixture.

In the embodiment shown in FIG. 1, the first heat exchangers 12 in the individual refrigerant circuits 10a, 10b are arranged downstream of the compressor 11 and upstream of the expansion valve 13 along a direction of flow of the respective refrigerant. Therefore, the first heat exchanger 12 is used in this example as a heat sink for the respective refrigerant circuit 10a, 10b. The first heat exchangers 12 are "heat sink side" heat exchangers in this sense. They are set up to give off heat from the respective refrigerant circuit 10a, 10b to the first heat transport fluid, which flows through the first changeover device 20.

The second heat exchangers 14 are arranged in the individual refrigerant circuits 10a, 10b along the flow direction of the respective refrigerant behind the expansion valve 13 and in front of the compressor 11. In this example, the second heat exchangers 14 therefore serve as a heat source for the respective refrigerant circuit 10a, 10b. The first heat exchangers 14 are "heat source side" heat exchangers in this sense. They are set up to give off heat from the second heat transport fluid, which flows through the second switching device 40, to the refrigerant of the respective refrigerant circuit 10a, 10b.

The first switching device 20 is set up to switch the first heat exchangers 12 of the refrigerant circuits 10a, 10b either in series one behind the other or parallel to one another between the first fluid connection 21 and the second fluid connection 22.

The first switching device 20 comprises a first device for flow diversion and a second device for flow diversion, here for example a first three-way valve 23 and a second three-way valve 24. There is a direct fluid connection between a B port via a line 25 of the first three-way valve 23 and a B port of the second three-way valve 24.

A AB connection of the first three-way valve 23 of the first changeover device 20 is in direct fluid communication (by means of a line 26) with a heat transport fluid outlet of the first heat exchanger 12 of the first refrigerant circuit 10a (on the left in FIG. 2). An A port of this first three-way valve 23 is in direct fluid communication (by means of a line 28) with the second fluid port 22.

A AB port of the second three-way valve 24 of the first switching device 20 is in direct fluid communication (by means of a line 27) with a heat transport fluid inlet of the first heat exchanger 12 of the second refrigerant circuit 10b (right side in FIG. 2). An A port of this second three-way valve 24 is in direct fluid communication (via a line 29) with the first fluid port 21.

A heat transfer fluid inlet of the first heat exchanger 12 of the first refrigerant circuit 10a is in direct fluid communication (via a line 31) with the first fluid port 21 and a heat transfer fluid outlet of the first heat exchanger 12 of the second refrigerant circuit 10b is in direct fluid communication (via a line 32). with the second fluid connection 22. These two direct fluid connections exist independently of the switching state of the first switching device 20.

In the first switching device 20, the first three-way valve 23, the second three-way valve 24 together with the lines 25, 26, 27 form a switchable direct fluid connection between the two first heat exchangers 12 of the two adjacent refrigerant circuits 10a, 10b.

In a series connection state shown in Fig. 2 of this switchable direct fluid connection between the first heat exchangers 12, the first three-way valve 23 of the first switching device 20 connects its AB port to its B port and the second three-way valve 24 the first switching device 20 connects its AB port to its B port. As a result (by means of the line 26, this first three-way valve 23, the line 25, this second three-way valve 24 and the line 27) there is a direct fluid connection between the heat transport fluid outlet of the first heat exchanger 12 of the first refrigerant circuit 10a and the heat transport fluid inlet of the first heat exchanger 12 of the second refrigerant circuit 10b.

This established direct fluid connection is shown schematically in FIG. 2 by an arrow 33 .

In Fig. 2, the A connection of the first three-way valve 23 is closed in the first switching device 20 and interrupts or blocks the direct fluid connection between the heat transport fluid outlet of the first heat exchanger 12 of the first refrigerant circuit 10a and the second fluid connection 22. Furthermore, the A port of the second three-way valve 24 of the first switching device 20 is closed and interrupts or blocks the direct fluid connection between the heat transport fluid inlet of the first heat exchanger 12 of the second refrigerant circuit 10b and the first fluid port 21 .

In the series connection state shown in FIG. 2, the first heat exchangers 12 of the two adjacent refrigerant circuits 10a, 10b for the first heat transport fluid are consequently connected in series between the first fluid connection 21 and the second fluid connection 22. The first heat exchangers 12 of the two refrigerant circuits 10a, 10b follow one another along a flow direction of the first heat transport fluid.

In a parallel circuit state of the switchable direct fluid connection for the first heat exchangers 12 shown in Fig. 3, the first three-way valve 23 of the first switching device 20 connects its AB port to its A port and the second three-way valve 24 the first switching device 20 connects its AB port to its A port. As a result, a direct fluid connection between the heat transport fluid outlet of the first heat exchanger 12 of the first refrigerant circuit 10a and the second fluid connection 22 is established (by means of the line 26, this first three-way valve 23 and the line 28). In Fig. 3 this established direct fluid connection is

tion shown schematically by an arrow 34; in Fig. 2, however, this direct fluid connection is blocked by this first three-way valve 23 and thus interrupted.

In addition, in Fig. 3 (by means of the line 29, the second three-way valve 24 and the line 27 of the first switching device 20) there is a direct fluid connection between the heat transport fluid inlet of the first heat exchanger 12 of the second refrigerant circuit 10b and the first fluid connection 21 manufactured. In Figure 3 this established direct fluid connection is shown schematically by an arrow 35; in Fig. 2, however, it is blocked by this second three-way valve 24 and thus interrupted.

In FIG. 3, the B port of the first three-way valve 23 in the first switching device 20 is closed. Furthermore, the B port of the second three-way valve 24 is closed. As a result, the switchable direct fluid connection shown in Fig. 2 (see arrow 33 in Fig. 2) between the heat transport fluid outlet of the first heat exchanger 12 of the first refrigerant circuit 10a and the heat transport fluid inlet of the first heat exchanger 12 of the second refrigerant circuit 10b (via the lines 25, 26, 27 and the three-way valves 23, 24) blocked and thus interrupted.

In FIG. 3, the first heat exchangers 12 of the two adjacent refrigerant circuits 10a, 10b for the first heat transport fluid are consequently connected in parallel between the first fluid connection 21 and the second fluid connection 22. The flow of the first heat transport fluid is divided in the first switching device 20 at a branching point 36 into two partial flows, one of the partial flows flowing only through the first heat exchanger 12 of the first refrigerant circuit 10a and another of the partial flows only through the first heat exchanger

shear 12 of the second refrigerant circuit 10b flows. The partial streams are then combined again in the first switching device 20 at a branching point 37 .

The second switching device 40 is set up to switch the second heat exchangers 14 of the two adjacent or consecutive refrigerant circuits 10a, 10b either in series one behind the other or parallel to one another between the third fluid connection 41 and the fourth fluid connection 42.

The second switching device 40 is constructed analogously to the first switching device 20 . It comprises a first device for diverting flow and a second device for diverting flow, here for example a first three-way valve 43 and a second three-way valve 44. Via a line 45 there is a direct fluid connection between a B port of these first three -way valve 43 and a B port of this second three-way valve 44.

A AB connection of the first three-way valve 43 of the second changeover device 40 is in direct fluid communication (by means of a line 46) with a heat transport fluid outlet of the second heat exchanger 14 of the first refrigerant circuit 10a (on the left in FIG. 2). An A port of this first three-way valve 43 is in direct fluid communication (by means of a line 48) with the fourth fluid port 42.

A AB port of the second three-way valve 44 of the second switching device 40 is in direct fluid communication (by means of a line 47) with a heat transport fluid inlet of the second heat exchanger 14 of the second refrigerant circuit 10b (right side in FIG. 2). A A connection of this second

The three-way valve 44 is in direct fluid communication with the third fluid port 41 (via a line 49 ).

A heat transport fluid inlet of the second heat exchanger 14 of the first refrigerant circuit 10a is in direct fluid communication (via a line 51) with the third fluid port 41 and a heat transport fluid outlet of the second heat exchanger 14 of the second refrigerant circuit 10b is in direct fluid communication (via a line 52). with the fourth fluid connection 42. These two direct fluid connections exist independently of the switching state of the second switching device 40.

In the second switching device 40, the first three-way valve 43 and the second three-way valve 44 together with the lines 45, 46, 47 form a switchable direct fluid connection between the two second heat exchangers 14 of the two adjacent refrigerant circuits 10a, 10b.

In a series connection state of this switchable direct fluid connection shown in FIG. 2, the first three-way valve 43 of the second switching device 40 connects its AB port to its B port and the second three-way valve 44 of the second switching device 40 connects its AB port to its B port. Thereby (by means of the line 46, this first three-way valve 43, the line 45, this second three-way valve 44 and the line 47) there is a direct fluid connection between the heat transport fluid outlet of the second heat exchanger 14 of the first refrigerant circuit 10a and the heat transport fluid inlet of the second heat exchanger 14 of the second refrigerant circuit 10b. This established direct fluid connection is shown schematically in FIG. 2 by an arrow 53 .

The A port of the first three-way valve 43 of the second switching device 40 is closed in FIG. 2 and interrupts or blocks the immediate

Fluid connection between the heat transport fluid outlet of the second heat exchanger 14 of the first refrigerant circuit 10a and the fourth fluid connection 42. Furthermore, the A connection of the second three-way valve 44 of the second switching device 40 is closed and interrupts or blocks the direct fluid connection between the heat transport fluid -Inlet of the second heat exchanger 14 of the second refrigerant circuit 10b and the third fluid connection 41.

In the series connection state of the switchable direct fluid connection shown in FIG. The second heat exchangers 14 of the two refrigerant circuits 10a, 10b follow one another along a flow direction of the second heat transport fluid.

In a parallel connection state shown in Fig. 3 for the second heat exchanger 14, the first three-way valve 43 of the second switching device 40 connects its AB port to its A port and the second three-way valve 44 of the second switching device 40 connects its AB port to its A port. As a result, a direct fluid connection between the heat transport fluid outlet of the second heat exchanger 14 of the first refrigerant circuit 10a and the fourth fluid connection 42 is established (by means of the line 46, the first three-way valve 43 and the line 48). This direct fluid connection is shown schematically in Figure 3 by arrow 54; in Fig. 2, however, it is blocked by the first three-way valve 43 of the second switching device 40 and thus interrupted.

In addition, a direct fluid connection between the heat transport fluid inlet of the second heat exchanger 14 of the second refrigerant circuit 10b and the third fluid connection 41 is established (by means of the line 47, the second three-way valve 44 and the line 49 of the second switching device 40). In Figure 2, this established direct fluid connection is shown schematically by an arrow 55; in FIG. 2, on the other hand, it is blocked by the second three-way valve 44 of the second switching device 40 and is thus interrupted.

The B port of the first three-way valve 43 of the second switching device 40 is closed in the parallel connection state shown in FIG. 3 . Furthermore, the B port of the second three-way valve 44 is closed. As a result, the direct fluid connection shown in Fig. 2 (see arrow 53 in Fig. 2) between the heat transport fluid outlet of the second heat exchanger 14 of the first refrigerant circuit 10a and the heat transport fluid inlet of the second heat exchanger 14 of the last refrigerant circuit 10b (via the lines 45 , 46, 47 and the three-way valves 43, 44) blocked and thus interrupted.

In the parallel connection state shown in FIG. 3, the second heat exchangers 14 of the two adjacent refrigerant circuits 10a, 10b for the second heat transport fluid are consequently connected in parallel between the third fluid connection 41 and the second fluid connection 42. The flow of the second heat transport fluid is divided at a branching point 56 in the second switching device 40 into two partial flows, with one of the partial flows flowing only through the second heat exchanger 14 of the first refrigerant circuit 10a and another of the partial flows only through the second heat exchanger 14 of the second refrigerant circuit 10b flows. Thereafter, these partial streams are brought together again at a branching point 57 in the second switching device 40 .

The refrigerant circuit device 1 from Fig. 1 can also switch the first heat exchangers 12 of the two adjacent refrigerant circuits 10a, 10b for the first heat transport fluid - as shown in Fig. 2 - in series between the first fluid connection 21 and the second fluid connection 22 and at the same time the second heat exchangers 14 of the two adjacent refrigerant circuits 10a, 10b--as shown in FIG. 3--connect parallel to one another between the third fluid connection 41 and the fourth fluid connection 42.

In addition, the refrigerant circuit device 1 from Fig. 1 can switch the first heat exchangers 12 of the two adjacent refrigerant circuits 10a, 10b for the first heat transport fluid - as shown in Fig. 3 - parallel to one another between the first fluid connection 21 and the second fluid connection 22 and at the same time the second heat exchangers 14 of the two adjacent refrigerant circuits 10a, 10b--as shown in FIG. 2--connect in series with one another between the third fluid connection 41 and the fourth fluid connection 42. A total of four different overall circuit states are therefore possible.

In the refrigerant circulation device 1, the first switching device 20 can optionally include at least one pump 61 for (the first) heat-transporting fluid. Advantageously, the refrigerant circuit device 1 comprises at least one pump 61 for each of the first heat exchangers 12. For example, the respective pump 61--as shown in FIG. alternatively behind.

Alternatively or additionally, the second switching device 40 can optionally include at least one pump 62 for (the second) heat transport fluid. The refrigerant cycle device 1 advantageously comprises at least one pump 62 for each of the second heat exchangers 14. For example, the respective pump 62—as shown in FIG

(the second) heat transport fluid may be inserted immediately before the corresponding second heat exchanger 14, alternatively after it.

Fig. 4 shows a second embodiment of a refrigerant circuit device 100 according to the invention with three independent internal refrigerant circuits 10a, 10b, 10c. The same components and assemblies are given the same reference numbers, are constructed identically and have the same function as in the refrigerant circuit device 1 unless otherwise described or is evident from the context. A last refrigerant circuit 10c (on the right in FIG. 4) is constructed like the other two refrigerant circuits 10a, 10b.

A first switching device 120 is set up to

- The first heat exchanger 12 of the first refrigerant circuit 10a (on the left in Fig. 4) and the second refrigerant circuit 10b (middle in Fig. 4), which follow one another, either in series one behind the other or parallel to one another between the first fluid connection 21 and the second fluid connection 22 switch as well

- The first heat exchanger 12 of the second refrigerant circuit 10b (middle in Fig. 4) and the last refrigerant circuit 10c (right in Fig. 4), which follow one another, either in series one behind the other or parallel to one another between the first fluid connection 21 and the second fluid connection 22 switch.

The first switching device 120 alone thus allows a total of four different switching states. Among other things, it can optionally connect all first heat exchangers 12 in series between the first fluid connection 21 and the second fluid connection 22 or connect all first heat exchangers 12 in parallel to one another between the first fluid connection 21 and the second fluid connection 22 .

As in the refrigeration cycle device 1, the first switching device 120 for the first refrigerant circuit 10a and the adjacent second refrigerant circuit 10b which follow each other comprises a first three-way valve 23 and a second three-way valve 24 whose AB ports (by means of a Line 25) are in direct fluid connection. In addition, the first changeover device 120 for the second refrigerant circuit 10b and the adjacent last refrigerant circuit 10c, which follow one another, comprises a further first three-way valve 23 and a further second three-way valve 24.

In the other first three-way valve 23 of the first switching device 120, its A port is in direct fluid communication (by means of a further line 28) with the second fluid port 22 and its AB port is in direct fluid communication (by means of a further line 26). with a heat transfer fluid outlet of the first heat exchanger 12 of the second refrigerant circuit 10b.

In the further second three-way valve 24 of the first switchover device 120, its A connection (by means of a line 29) is in direct fluid connection with the first fluid connection 21 and its AB connection is (by means of a further line 27) in direct fluid connection Fluid connection with a heat metransportfluid inlet of the first heat exchanger 12 of the last refrigerant circuit 10c.

In FIG. 3, the further first three-way valve 23, the further second three-way valve 24 and the further lines 25, 26, 27 form a further switchable direct fluid connection of the first switching device 120, specifically between the first heat exchangers 12 of the second refrigerant circuit 10b and the last refrigerant circuit 10c.

In the refrigerant circuit device 100, the heat transport fluid inlet of the first heat exchanger 12 of the first refrigerant circuit 10a is always in direct fluid connection with the first fluid connection 21, regardless of the switching states of the first switching device 120 (by means of the line 31). Furthermore, a heat transport fluid outlet of the first heat exchanger 12 of the last refrigerant circuit 10c is always in direct fluid connection with the second fluid connection 22, regardless of the switching states of the first switching device 120 (by means of the line 32).

In other words, in the first switching device 120, all the first three-way valves 23 are connected in parallel (via their A ports) to the second fluid port 22, and all the second three-way valves 24 are connected in parallel (via their A ports). connected to the first fluid port 21 . One of the first three-way valves 23 is connected to the heat transport fluid outlets of the first heat exchangers 12 by means of its AB connection. No first three-way valve is connected only to the heat transport fluid outlet of the first heat exchanger 12 of the last refrigerant circuit 10c. One of the second three-way valves 24 is connected to the heat transport fluid inlets of the first heat exchangers 12 by means of its AB connection. No second three-way valve is connected only to the heat transport fluid inlet of the first heat exchanger 12 of the first refrigerant circuit 10a. The B-ports of the first three-way valves 23 are each connected (by means of line 25) to the B-port of the second three-way valve 24, which (by means of its AB-port) to the heat transport fluid inlet of the subsequent Refrigerant circuit 10b or 10c is connected.

The second switchover device 140 of the refrigeration cycle device 100 is expanded analogously to the first switchover device 120. A separate, detailed description is therefore dispensed with.

The second switching device 140 alone allows a total of four different switching states. Among other things, it can optionally connect all second heat exchangers 14 in series between the third fluid connection 41 and the fourth fluid connection 42 or connect all second heat exchangers 42 in parallel to one another between the third fluid connection 41 and the fourth fluid connection 42 .

The refrigeration cycle device 100 in FIG. 4 enables up to sixteen different overall switching states (four switching states of the first switching device 120 times four switching states of the second switching device 140). For example, the first heat exchanger 12 of the first refrigerant circuit 10a and the second refrigerant circuit 10b can be connected in series between the first fluid connection 21 and the second fluid connection 22, while the first heat exchanger 12 of the last refrigerant circuit 10c is connected in parallel to the series connection of the other two first heat exchangers 12 between the first fluid port 21 and the second fluid port 22 is connected. At the same time, the second heat exchanger 14 of the second refrigerant circuit 10b and the third refrigerant circuit 10c can be connected in series between the third fluid connection 41 and the fourth fluid connection 42, while the second heat exchanger 14 of the first refrigerant circuit 10a is connected in parallel to the series connection of the other two second heat exchangers 14 between the third fluid port 41 and the fourth fluid port 42 is connected. Such an overall circuit state can be useful, among other things, when different refrigerants are used in the various refrigerant circuits 10a, 10b, 10c. Different refrigerants can be particularly suitable for different temperatures on the heat source side, different temperatures on the heat sink side and/or different temperature gradients.

The refrigerant circuit device 100 shown in FIG. 4 can be expanded in a simple manner by any number of additional refrigerant circuits. For this purpose, any number of center modules MM can simply be inserted between the first refrigerant circuit 10a and the last refrigerant circuit 10c. With a modular design, different refrigerant circuit devices with different numbers of internal refrigerant circuits 10a, 10b, 10c can be implemented in a simple manner.

For example, let N be a number of center modules MM. Then, for the refrigerant cycle device 1 in FIG. 1 , the number N=0 (no center module MM) and for the refrigerant cycle device 100 the number N=1 (one center module MM). Of course, by adding a further central module MM to the refrigerant circuit device 100, a refrigerant circuit device with N=2 central modules MM can be implemented, ie with a total of four refrigerant circuits (not shown). By adding further middle modules MM, for example, a refrigeration circuit device with N=18 middle modules MM can be implemented, ie with a total of 20 refrigeration circuits (not shown) and the like.

With a number of N central modules, there are at least 2 ² ' ^(N+1) different overall circuit states.

In fact, there may be other switching states. The first switching device 120 of the refrigerant circuit device 1 shown in FIG. 4 additionally makes it possible to selectively switch individual, multiple, or all first heat exchangers 12 between the first fluid connection 21 and the second fluid connection 22 .

For example, if the first three-way valve 23 on the left in FIG. 4 (above the first refrigerant circuit 10a) connects its AB port to its B port

connects and at the same time the second three-way valve 24 in the middle in Fig. 4 (above the second refrigerant circuit 10b) connects its AB connection to its A connection, then no heat transport fluid can flow from the first fluid connection 21 through the first heat exchanger 12 of the first refrigerant circuit 10a flow to the second fluid connection 22 . The first switching device 120 has switched off this first heat exchanger 12 .

Similarly, the first switching device 120 can selectively switch off the first heat exchanger 12 of the second refrigerant circuit 10b. This first heat exchanger 12 is then connected neither in parallel nor in series between the first fluid connection 21 and the second fluid connection 22 . For this purpose, the first three-way valve 23 in the middle of Fig. 4 (above the second refrigerant circuit 10b) connects its AB port to its B port, whereas this second three-way valve 24 connects its AB port to its A - Connection and thus with the first fluid port 21 connects.

Furthermore, the first switching device 120 can selectively switch off the first heat exchanger 12 of the last refrigerant circuit 10c. This first heat exchanger 12 is then connected neither in parallel nor in series between the first fluid connection 21 and the second fluid connection 22 . For this purpose, the first three-way valve 23 in the middle of Fig. 4 (above the second refrigerant circuit 10b) connects its AB port to its A port and thus to the second fluid port 22, whereas the second three-way valve 24 on the right in FIG. 4 (above the last refrigerant circuit 10c) connects its AB connection to its B connection.

Correspondingly, the second switching device 140 is additionally set up to switch either the second heat exchanger 14 of the first refrigerant circuit 10a, the second heat exchanger 14 of the second refrigerant circuit 10b and/or

switch off the second heat exchanger 14 of the last refrigerant circuit 10c.

If one of the refrigerant circuits 10a, 10b, 10c is not operated, for example because it is not needed to meet the current performance requirements, its first heat exchanger 12 and/or its second heat exchanger 14 can be switched from the respective heat transport fluid circuit. This lowers the flow resistance and increases efficiency in this situation.

One, several or all of the three-way valves 23, 24, 43, 44 can be designed as a three-way switching valve. One, several or all of the three-way valves 23, 24, 43, 44 can be designed as a mixing valve, in particular as a controllable mixing valve.

In general, the invention is not limited to the use of three-way valves.

One way of modifying the refrigerant circuit device 100 from FIG. 4 is to replace the two three-way valves 23, 24 of the first switching device 120 in the central module MM with a suitable 6/4-way valve (not shown). Alternatively or additionally, the two three-way valves 43, 44 of the second switching device 140 in the center module MM can be replaced by a suitable 6/4-way valve (not shown).

Fig. 5 shows a third embodiment of a refrigerant circuit device 200 according to the invention. The refrigerant circuit device 200 from Fig. 5 differs from the refrigerant circuit device 100 from Fig middle modules MM). Second include

the switchable direct fluid connections of a first switching device 220 between the first heat exchangers 12 of successive refrigerant circuits 10a, 10b, 10c, 10d instead of two three-way valves 23, 24 each have a 4/2-way valve 223. Thirdly, the switchable direct fluid connections include a second changeover device 240 between the second heat exchangers 14 of successive refrigerant circuits 10a, 10b, 10c, 10d instead of two three-way valves 43, 44 each have a 4/2-way valve 243. Otherwise, the refrigerant circuit device 200 from Fig. 5 corresponds to the refrigerant circuit device 100 from Fig. 4.

In the four-way valves 223 of the first switching device 220, a first valve connection (by means of a line 226) is connected to a heat transport fluid outlet of the first heat exchanger 12 of one of the successive refrigerant circuits 10a, 10b, 10c, a second valve connection is (by means of a line 228) to the second fluid port 22, a third valve port is connected (by means of a line 229) to the first fluid port 21 and a fourth valve port is (by means of a line 227) to the heat transport fluid inlet of the first heat exchanger 12 of the other of the successive refrigerant circuits 10b, 10c, 10d connected. In its first valve position, the respective four-way valve 223 connects its first valve port to its fourth port (series connection state). In the first valve position, the second valve port and the third valve port can be blocked. In its second valve position, it connects its first valve port to its second valve port and its third valve port to its fourth valve port (parallel connection state).

In the four-way valves 243 of the second switching device 240, a first valve connection (by means of a line 246) is connected to a heat transport

fluid outlet of the second heat exchanger 14 of one of the successive refrigerant circuits 10a, 10b, 10c, a second valve port is connected (by means of a line 248) to the fourth fluid port 42, a third valve port is (by means of a line 249) to the third fluid port 41 and a fourth valve port is connected (by means of a line 247) to the heat transport fluid inlet of the second heat exchanger 14 of the other of the successive refrigerant circuits 10b, 10c, 10d. In its first valve position, the respective four-way valve 243 connects a first valve port to its fourth port (series connection state). In the first valve position, the second valve port and the third valve port can be blocked. In its second valve position, it connects its first valve port to its second valve port and its third valve port to its fourth valve port (parallel connection state).

In developments of the refrigerant circuit device 200 that are not shown, the use of four-way valves with blocking positions and/or the use of additional blocking valves in the first changeover device 220 enables further switching states in which a flow through one or more of the first heat exchangers 12 with the first Heat transfer fluid is completely blocked. Accordingly, the use of four-way valves with blocking positions and/or the use of additional blocking valves in the second switching device 240 enables further switching states in which the second heat transport fluid is completely blocked from flowing through one or more of the second heat exchangers 14 .

5 shows the refrigerant circuit device 200 in an overall switching state, in which all first heat exchangers 12 are connected in parallel to one another between the first fluid connection 21 and the second fluid connection 22.

while all second heat exchangers 14 are connected in series between the third fluid port 41 and the fourth fluid port 42 .

Of course, one or more pumps 61 , 62 for (the first and/or second) heat transport fluid can be formed in the refrigerant circuit device 100 in FIG. 4 and refrigerant circuit 200 in FIG. 5 as in the refrigerant circuit device 1 in FIG. 6 (not shown).

Fig. 6 shows a first embodiment of a thermal management system 300 according to the invention for a passenger car with an electric drive with the refrigerant circuit device 1 from FIG. 1 with the optional pump devices 61, 62.

The thermal management system 300 includes an outdoor heat exchanger 304, an HVAC unit 320, a battery heat exchanger module 330 and an electronic heat exchanger module 340.

The external heat exchanger 304 can be designed as a radiator, in particular as a radiator for the exchange between heat transport fluid and ambient air.

The HVAC unit includes an HVAC heat absorber 321 for cooling air for a vehicle compartment, an HVAC radiator 323 for heating air for the vehicle compartment, and an air mix door 325 for controlling a proportion of air for the vehicle compartment that the HVAC radiator 323 flows through.

The thermal management system 300 is set up to form a first heat transport fluid circuit 301 on the heat sink side with at least one heat sink and a second heat transport fluid circuit 310 on the heat source side with at least one heat source.

The thermal management system 300 is very flexible and set up to execute different modes of operation. In Fig. 6, the heat management is in a cooling mode for cooling the vehicle interior, in Fig. 7 in a heat pump mode for heating the vehicle interior using the ambient air as a heat source as well as on-board heat sources, in Fig. 8 in a heat pump mode for heating the vehicle interior using only the ambient air as a heat source, in Fig. 9 in a post-heating mode and in Fig. 10 a pure outdoor cooling mode.

An "inner" part of the first heat transport fluid circuit 301 is formed by the first switching device 20 of the refrigerant cycle device 1 with the first heat exchangers 12 . An "external" part of the first heat transfer fluid circuit 301 is connected to the first fluid port 21 and to the second fluid port 22 and includes a pump 302 for (the first) heat fluid. The external heat exchanger 304 and/or the HVAC unit 320 can be optionally integrated into the first heat transport fluid circuit 301 as a heat sink via a switching device of the first heat transport fluid circuit 301 . In the embodiment shown, the switching device of the first heat transport fluid circuit 301 includes a three-way valve 303 via which the external heat exchanger 304 and the HVAC radiator 323 are connected in parallel to the second fluid connection 22 . If the three-way valve 303 is designed as a mixing valve, the HVAC unit 320 (in particular the HVAC radiator 323) and the outdoor heat exchanger 304 can optionally be integrated into the first heat transport fluid circuit 301 at the same time as heat sinks.

An "inner" part of the second heat transport fluid circuit 310 is formed by the second switching device 40 of the refrigerant circuit device 1 with the second heat exchangers 14 . An "outer" part of the second heat transport

Fluid circuit 310 is connected to the third fluid port 41 and to the fourth fluid port 42 and includes a pump 311 for (the second) heat transfer fluid. The external heat exchanger 304, the HVAC unit 320 (more precisely, the HVAC heat absorber), a vehicle battery 332 and/or electronics 342 can be integrated as heat source(s) in the second heat transport fluid circuit 301 via a switching device of the second heat transport fluid circuit 310. In the embodiment shown, the switching device of the first heat transport fluid circuit 310 comprises a plurality of flow diversion devices, here for example a plurality of three-way valves 312, 313, 314, 331, 341. One, more or all of the flow diversion devices can optionally enable flow regulation. Furthermore, the switching device of the first heat transport fluid circuit here includes a solenoid valve 329. By designing one or more of the devices for flow diversion or the three-way valves 312, 313, 314, 313, 341 as mixing valves, there is greater flexibility for simultaneous Integration of several of the components mentioned in the second heat transfer fluid circuit 310 allows.

The battery heat exchanger module 330 includes a device for flow diversion, the vehicle battery 332 and an internal auxiliary circuit with a pump 333 for (the second) heat transport fluid, an electric heater 334 and a check valve 335. Through the switching device of the second heat transport fluid circuit 310, more precisely through the device for flow diversion of the battery heat exchanger module 330, the second heat transfer fluid can be selectively routed through the vehicle battery 332 or via a battery bypass 336 to the vehicle battery 332 past. Here, the device for diverting the flow of the battery heat exchanger module 330 is designed as a three-way valve 331, for example. If the three-way valve 331 is designed as a (controllable) mixing valve, the second heat transfer fluid can also partially flow through the vehicle battery 332 and at the same time

partially routed past the vehicle battery 332 via the battery bypass 336 . In a development that is not shown, the switching device of the first heat transport fluid circuit 301 makes it possible to integrate the vehicle battery 332 into the first heat transport fluid circuit 301 if required.

There are also electric vehicles and hybrid vehicles in which the vehicle battery is only cooled directly by the environment, for example by means of ambient air. In this case, the battery heat exchanger module 330 is not required.

The electronics heat exchanger module 340 comprises a device for flow diversion, the electronics 342 and an internal auxiliary circuit with a pump 343 for (the second) heat transport fluid and a check valve 345. The electronics 342 can comprise one or more power electronics, for example power electronics for an electric motor of the vehicle and/or power electronics for charging the vehicle battery 332. Through the switching device of the second heat transport fluid circuit 310, more precisely through the device for redirecting the flow of the electronic heat exchanger module 340, the second heat transport fluid can be switched through the electronics 342 or be routed past the electronics 342 via an electronics bypass 346 . Here the device for diverting the flow of the battery heat exchanger module 330 is designed as a three-way valve 331, for example. If the three-way valve 341 is embodied as a (controllable) mixing valve, the second heat transport fluid can also be routed partially through the electronics 342 and partially via the electronics bypass 346 past the electronics 342 at the same time. In a development that is not shown, the switching device of the first heat transport fluid circuit 301 makes it possible to integrate the electronics 342 into the first heat transport fluid circuit 301 if required.

Similar to the battery heat exchanger module 330, the electronic heat exchanger module 340 is generally optional.

In the cooling mode shown in FIG. 6 for cooling the vehicle interior, (only) the HVAC heat absorber 321 is integrated into the second heat transport fluid circuit 310 . More specifically, the second heat transport fluid flows through the HVAC heat absorber 321 . Air introduced into the vehicle interior passes through the HVAC heat absorber 321 beforehand. There it gives off heat to the second heat transport fluid. This cools the air. Here, the HVAC heat absorber 321 serves as a heat source for the second heat transport fluid circuit 310 and thus for the refrigerant device 1. The air can be air from the outside (fresh air) and/or air from the vehicle interior (recirculated air).

The second heat transport fluid transports the absorbed heat into the refrigerant circuit device 1, more precisely via the second switching device 40 into at least one of the second heat exchangers 14. There the heat is pumped through the respective refrigerant circuit 10a, 10b to the respective first heat exchanger 12. There, the first heat transport fluid absorbs the heat.

In the cooling mode in FIG. 6 , the outdoor heat exchanger 304 is (only) integrated into the first heat transport fluid circuit 301 . The first heat transport fluid transports heat from the first heat exchangers 12 to the outdoor heat exchanger 304. Heat is released to the ambient air via the outdoor heat exchanger 304. The outdoor heat exchanger 304 serves as a heat sink here.

In the heating mode shown in FIG. 7, the external heat exchanger 304, the vehicle battery 332 and the electronics 342 are integrated into the second heat transport fluid circuit 310 as heat sources. Furthermore, the HVAC unit 320 as

Heat sink in the first heat transfer fluid circuit 301 involved. To this end, the first heat transport fluid flows through the HVAC radiator 323. The air mix damper 325 is adjusted so that all of the air for the vehicle interior which flows through the HVAC unit 320 flows through the HVAC radiator 323 in order to enable good heat transfer.

The HVAC unit 320 here also includes an HVAC switching device that makes it possible, in addition to the HVAC radiator 323, to also integrate the HVAC heat absorber 321 for heating the air for the vehicle interior as a heat sink in the first heat transport fluid circuit 301. In this exemplary embodiment, HVAC switching device includes a three-way valve 24 and a solenoid valve 322. The HVAC switching device is configured to connect the HVAC heat absorber 321 and the HVAC radiator 323 in series for heat transport fluid. In a further development that is not shown, the HVAC switching device is also set up to use the HVAC radiator 323 in addition to the HVAC heat absorber 321 to cool the air for the vehicle interior, for example by the HVAC switching device using the HVAC radiator 323 in addition to the HVAC heat absorber 321 in the second heat transport fluid circuit 310 incorporates.

In the heating mode according to FIG. 7 , the thermal management system works as a heat pump in order to pump heat from the outside air, the vehicle battery 332 and the electronics 342 into the vehicle interior via the refrigerant circuit device 1 .

In the first heat transport fluid circuit 301, a temperature sensor can be arranged upstream of the HVAC radiator 323 in the direction of flow, embodied here as a PTC sensor 306. The abbreviation PTC stands for the English term "Positive Temperature Coefficient Thermistor" and designates a PTC thermistor.

In the internal source heating mode shown in FIG. 8, only the vehicle battery 332 and the electronics 342 are integrated into the second heat transport fluid circuit 310 as heat sources. Unlike in FIG. 7 , the outdoor heat exchanger 304 is not integrated into the second heat transport fluid circuit 310 . The three-way valves 313 and 314 prevent the second heat-transporting fluid from flowing through the outdoor heat exchanger. Otherwise, the heating mode in FIG. 8 corresponds to the heating mode shown in FIG.

9 shows the thermal management system 300 in the post-heat mode. The air for the vehicle interior is first cooled by the HVAC heat absorber 321 in the HVAC unit 320 . Humidity can condense in the process. Thereafter, the air is guided through the HVAC radiator 323 by means of the air mix door 325 . The HVAC radiator 323 reheats the air. At the same time, the relative humidity drops. The reheat mode ensures good dehumidification of the air for the vehicle interior. Thus, for example, the fogging of vehicle windows can be reduced or prevented.

In the reheat mode, the HVAC heat absorber 321 is included as a heat source in the second heat transfer fluid circuit 310 and the HVAC radiator 323 is included as a heat sink in the first heat transfer fluid circuit 301 .

Depending on the operating conditions, for example the vehicle battery 332 and/or the electronics 342 can be switched on in FIG. 9 as additional heat sources in the second heat transport fluid circuit 310 .

Depending on the required performance, the operating conditions and optionally depending on possibly different refrigerants in the refrigerant circuits 10a, 10b, in the operating modes shown in FIGS

the first heat exchangers 12 are optionally switched in parallel or in series between the first fluid port 21 and the second fluid port 22 by the first switching device 20 . In addition, the second heat exchangers 14 can be selectively connected in parallel or in series between the third fluid port 41 and the fourth fluid port 42 by the second switching device 40 . In addition, the second refrigerant circuit 10b can optionally not be operated at all, be operated with a different capacity than or with the same capacity as the first refrigerant circuit 10a.

Optionally, the second heat transfer fluid circuit 310 includes a valve (designed here as a three-way valve 350) by means of which the inner part of the second heat transfer fluid circuit 310 can be blocked. FIG. 10 shows thermal management system 300 of FIG. 6 in an external cooling-only mode. The second heat transport fluid circulates only in the outer part of the second heat transport fluid circuit 310. The switching device of the second heat transport fluid circuit 310 also ensures that the second heat transport fluid flows through the external heat exchanger 304 to release heat and also through the vehicle battery 332 and/or the electronics 342 flows through to absorb heat. This mode allows for the vehicle battery 332 and/or electronics 342 to be easily, efficiently, and effectively cooled by releasing heat to the surrounding air. The first heat transport fluid circuit 301 and the refrigerant cycle device 1 are preferably turned off in the outdoor cooling-only mode.

Of course, instead of the refrigerant cycle device 1 shown in FIG. 1 , the thermal management system 300 may include the refrigerant cycle device 100 shown in FIG. 4 or the refrigerant cycle device 200 shown in FIG. 5 .

Not all circuit options of the thermal management system 300 are shown in FIGS. 6 to 10 . For example, in Fig. 7, the second heat transfer fluid

in the battery heat exchanger module 330 instead of only through the battery bypass 336 completely or partially through the vehicle battery 332 if the vehicle battery 332 is also to be cooled. As an alternative or in addition, the second heat transport fluid in the electronics heat exchanger module 340 can be passed entirely or partially through the electronics 342 instead of only through the electronics bypass 346 if the electronics 342 are also to be cooled.

11 shows a second embodiment of a heat management system 400 according to the invention for a passenger car with an electric drive. Deviating from the heat management system 300 from FIGS. 5 to 10, the refrigerant circuit 100 from FIG. 4 is integrated here. In addition, a switching device of a second heat transport fluid circuit 410 also offers the possibility of integrating a battery heat exchange unit 430 and an electronics heat exchange unit 440 either in parallel or in series in the second heat transport fluid circuit 410 . For this purpose, the switching device of the second heat transport fluid circuit 410 in FIG. 11 has additional valves, here by way of example two additional three-way valves 451, 452 in the form of mixing valves. Otherwise, the heat management system 400 shown in FIG. 11 has the same structure as the heat management system 300 shown in FIGS. 6 to 10. The same components are provided with the same reference numbers.

In FIG. 11, the thermal management system 400 is shown in an internal source heating mode using the vehicle battery and power electronics of the vehicle as heat sources. In contrast to the internal source heating mode of the heat management system 300 in FIG. 8, the vehicle battery 332 and the electronics 342 are not connected in series here one behind the other, but in parallel to one another in the second heat transport fluid circuit. Therefore, the second heat transport fluid flowing into the electronics 342 (at least

substantially) the same temperature as the second heat transfer fluid entering the vehicle battery 332 .

Of course, like the thermal management system 300 shown in FIGS. 6 to 10, the thermal management system 400 shown in FIG. 11 can be operated in a large number of different operating modes.

The thermal management system 300 and the thermal management system 400 can include additional modules that are not shown, for example at least one seat climate control module. Similar to the battery heat exchanger module 330, 430 and the electronics heat exchanger module 340, 440, it can be provided that the individual modules can be connected in parallel, in series and/or partially in parallel in the first heat transport fluid circuit 301 and/or in the second heat transport fluid circuit 310, 410 can be switched. Partially parallel means that partial flows of the heat transport fluid are each passed in parallel through different modules and that at least one partial flow is passed through at least two of the modules in series.

The present invention allows a very flexible operation of the respective refrigerant circuit 1, 100, 200. The adjustment of the first switching device 20, 120, 220 and / or the second switching device 40, 140, 240 and mutually directly independent operation of the inner refrigerant circuits 10a, 10b, 10c, 10d also enables high efficiency under a wide variety of power requirements, operating modes and operating conditions.

The embodiments described herein are primarily provided by way of example to describe and illustrate the invention in greater detail. The scope of the invention is defined in the claims and is generally not limited to the specific embodiments described.

Reference List

1, 100, 200 refrigerant cycle device

10a, 10b, 10c, 10d refrigerant circuit

11 compressor

12 first heat exchanger

13 expansion valve

14 second heat exchanger

20, 120, 220 first switching device

21 first fluid port

22 second fluid port

23 first three-way valve

24 second three-way valve

25, 26, 27, 28, 29 line

31, 32 line

33, 34, 35 arrows

36, 37 branch point

40, 140, 240 second switching device

41 third fluid port

42 fourth fluid port

43 first three-way valve

44 second three-way valve

45, 46, 27, 48, 49 line

51, 52 line

53, 54, 55 arrows

56, 57 branch point

61, 62 pump

223, 243 four-way valve

226, 227, 228, 229 line

246, 247, 248, 249 line

300, 400 thermal management system

301 first heat transfer fluid circuit

302, 311, 333, 343 pump

303, 305, 312, 313, 314 three-way valve

304 outdoor heat exchanger

306 PTC sensor

310, 410 second heat transport fluid circuit

320 HVAC unit

321 HVAC heat absorber

322, 329 solenoid valve

323 HVAC radiator

324, 331 , 341 , 350 three-way valve (device for flow diversion)

325 air mix door

330, 430 battery heat exchanger module

332 vehicle battery

334 electric heater

335, 345 check valve

336 battery bypass

340, 440 electronic heat exchanger module

342 electronics

346 electronics bypass

451, 452 three-way valve

MM middle module

Claims

63 patent claims:

1. Refrigerant circuit device (1; 100; 200) for a thermal management system (300; 400) for a vehicle, wherein the thermal management system (300; 400) transports heat by means of at least one heat transport fluid, comprising: at least two self-contained, internal refrigerant circuits (10a, 10b, 10c, 10d), wherein the refrigerant circuits (10a, 10b, 10c, 10d) respectively

- A first heat exchanger (12) for exchanging heat between the respective refrigerant circuit (10a, 10b, 10c, 10d) and heat transport fluid and

- A second heat exchanger (14) for exchanging heat between the respective refrigerant circuit (10a, 10b, 10c, 10d) and heat transport fluid and for pumping heat between the second heat exchanger (14) and the first heat exchanger (12) are set up; characterized by a first switching device (20; 120; 220) connected to the first heat exchanger (12) and having a first fluid connection (21) and a second fluid connection (22) for conducting heat transport fluid through the first heat exchanger (12); wherein the first switching device (20; 120; 220) is set up to switch the first heat exchangers (12) of the at least two refrigerant circuits (10a, 10b, 10c, 10d) either in series one behind the other or parallel to one another between the first fluid connection (21) and the to switch the second fluid connection (22). 64

2. Refrigerant circuit device (1; 100; 200) according to claim 1, characterized in that the first switching device (20; 120; 220) is located between first heat exchangers (12) of two consecutive ones of the at least two refrigerant circuits (10a, 10b, 10c, 10d) a switchable direct fluid connection (23, 24, 25, 26, 27; 223, 226, 227) for heat transport fluid, said switchable direct fluid connection (23, 24, 25, 26, 27; 223, 226, 227) for the heat transport fluid between the first heat exchangers (12) of the two successive refrigerant circuits (10a, 10b, 10c, 10d)

- is manufactured in its series connection state and

- is interrupted in its parallel circuit state and instead o a direct fluid connection (23, 26, 28; 223, 226, 229) for heat transport fluid between the first heat exchanger (12) of one of the two successive refrigerant circuits (10a, 10b, 10c, 10d) and the second fluid port (22), which it interrupts in its series connection state, and o establishes a direct fluid connection (24, 27, 29; 223, 227, 229) for the heat transport fluid between the first heat exchanger (12) of the other of the two successive refrigerant circuits (10a, 10b, 10c, 10d) and the first fluid connection (21), which interrupts them in their series connection state.

3. Refrigerant circuit device (1; 100) according to claim 2, characterized in that each switchable direct fluid connection (23, 24, 25, 26, 27) between the first heat exchangers (12) of two successive refrigerant circuits (10a, 10b, 10c) each have a first three-way valve (23) and a second three-way valve (24), the respective first three-way valve (23) being in direct fluid communication with 65

- the first heat exchanger (12) of one of the two successive refrigerant circuits (10a, 10b, 10c),

- The respective second three-way valve (24) and

- The second fluid connection (22), wherein the respective second three-way valve (24) is in direct fluid communication with

- the first heat exchanger (12) of the other of the two adjacent refrigerant circuits (10a, 10b, 10c),

- The respective first three-way valve (23) and

- The first fluid connection (21).

4. Refrigerant circuit device (1; 100; 200) according to one of the preceding claims, characterized in that the first heat exchanger (12) of a first of the at least two refrigerant circuits (10a, 10b, 10c, 10d) independently of the switching states of the first switching device (20 ; 120; 220) is in direct fluid connection (31) to the first fluid connection (21) and that the first heat exchanger (12) of the last of the at least two refrigerant circuits (10a, 10b, 10c, 10d) is independent of the switching states of the first switching device ( 20; 120; 220) is in direct fluid connection (32) with the second fluid connection (22).

5. Refrigerant cycle device (1; 100; 200) according to one of the preceding claims, characterized by a second switching device (40; 140; 240) connected to the second heat exchanger (14) and having a third fluid connection (41) and a fourth fluid connection (42) for passing external heat transfer fluid through the second heat exchangers (14); 66

wherein the second switching device (40; 140; 240) is set up to switch the second heat exchangers (14) of the at least two refrigerant circuits (10a, 10b, 10c, 10d) either in series one behind the other or parallel to one another between the third fluid connection (41) and the fourth fluid connection (42) to switch.

6. Refrigerant circuit device (1; 100; 200) according to one of the preceding claims, characterized in that the at least two refrigerant circuits (10a, 10b, 10c, 10d) can be operated independently of one another.

7. refrigerant circuit device (1; 100; 200) according to any one of the preceding claims, characterized in that the refrigerant circuit device (1; 100; 200) is adapted to one of the at least two refrigerant circuits (10a, 10b, 10c, 10d). to operate a stationary power and to operate another of the at least two refrigerant circuits (10a, 10b, 10c, 10d) with needs-based power.

8. Refrigerant cycle device (1; 100; 200) according to any one of the preceding claims, characterized in that a compressor (11) of at least one of the refrigerant circuits (10a, 10b, 10c, 10d) has a variable cubic capacity and/or or has a speed control.

9. Refrigerant circuit device (1; 100; 200) according to one of the preceding claims, characterized in that a first of the at least two refrigerant circuits (10a, 10b, 10c, 10d) comprises a first refrigerant and a second of the refrigerant circuits (10a, 10b, 10c , 10d) comprises a second refrigerant which differs from the first refrigerant.

10. Refrigerant circuit device (100; 200) according to any one of the preceding claims, characterized in that the refrigerant circuit device (100; 200) has at least three self-contained, internal refrigerant circuits (10a, 10b, 10c, 10d), the first switching device (120; 220) is set up to connect the first heat exchangers (12) of two consecutive ones of the at least three refrigerant circuits (10a, 10b, 10c, 10d) either in series one behind the other or parallel to one another between the first fluid connection (21) and the second fluid connection ( 22) to switch.

11. Refrigerant circuit device (100; 200) according to Claims 5 and 10, characterized in that the second switching device (40; 140; 240) is set up to switch the second heat exchangers (14) of two consecutive ones of the at least three refrigerant circuits (10a, 10b, 10c , 10d) to switch between the third fluid connection (41) and the fourth fluid connection (42) either in series one behind the other or parallel to one another.

12. Refrigerant circuit device (1; 100; 200) according to one of the preceding claims, characterized in that the internal refrigerant circuits (10a, 10b, 10c, 10d) are each designed as a compression heat pump, as an absorption heat pump, as an adsorption heat pump, as an electrocaloric heat pump or as a magnetocaloric heat pump are, wherein the individual refrigerant circuits (10a, 10b, 10c, 10d) can be designed differently from each other.

13. Refrigerant circuit device (1; 100) according to any one of the preceding claims, characterized in that the first switching device (20; 120) is also set up to selectively not switch individual first heat exchangers (12) at all between the first fluid connection (21) and the second To switch fluid connection (22).

14. Thermal management system (300; 400) for a vehicle, wherein the thermal management system (300; 400) is adapted to form a first heat transport fluid circuit (301) and a second heat transport fluid circuit (310, 410), characterized by a Refrigerant cycle device (1; 100; 200) according to one of the preceding claims, wherein the first switching device (20; 120; 220) is integrated into the first heat transport fluid circuit (301) and the second switching device (40; 140; 240) into the second Heat transport fluid circuit (310; 410) is involved.

15. Thermal management system (300; 400) according to claim 14, characterized by an HVAC unit (320) with an HVAC heat absorber (321) and an HVAC radiator (322), wherein the HVAC unit (320) has an HVAC switching device (322, 324), which is set up to optionally integrate the HVAC heat absorber (321) into the second heat transport fluid circuit (310; 410) or to integrate it together with the HVC radiator (322) into the first heat transport fluid circuit (301 ) to include.