Temperature control device for temperature control of at least a part of a motor vehicle, method for operating such a temperature control device and motor vehicle

Abstract

The invention relates to a temperature control device (6) for temperature control of at least a partial area of ​​a motor vehicle, comprising: - a refrigerant circuit (7) through which a refrigerant flows, which has: ◯ a refrigerant compressor (11) by means of which the refrigerant is to be conveyed and compressed; ◯ a condenser (14) for condensing the refrigerant; and ◯ at least one expansion valve (15) for expanding the refrigerant; and - a separating device (32) arranged in the refrigerant circuit (7) for separating a liquid phase (37) of the refrigerant from a gaseous phase of the refrigerant, wherein a heating element (33) for heating the refrigerant is integrated into the separating device (32).

Description

[0001] The invention relates to a temperature control device for controlling the temperature of at least one portion of a motor vehicle. Furthermore, the invention relates to a method for operating such a temperature control device. The invention also relates to a motor vehicle having at least one such temperature control device.

[0002] JP 5861 495 B2 discloses a temperature control device for a vehicle. Furthermore, EP 2 265 453 B1 discloses a cooling arrangement for cooling a temperature-sensitive component of a motor vehicle. Furthermore, DE 603 ​​20 060 T2 discloses a method for operating a cooling system.

[0003] The object of the present invention is to provide a temperature control device for temperature control of at least one partial area of ​​a motor vehicle, a method for operating such a temperature control device and a motor vehicle with at least one such temperature control device, so that a particularly efficient and robust operation of the temperature control device can be realized.

[0004] This object is achieved according to the invention by a temperature control device having the features of patent claim 1, by a method having the features of patent claim 10, and by a motor vehicle having the features of patent claim 11. Advantageous embodiments of the invention are the subject of the dependent claims.

[0005] A first aspect of the invention relates to a temperature control device for temperature control, i.e. for cooling and / or heating at least a partial region of a motor vehicle, also simply referred to as a vehicle. This means that the motor vehicle, also simply referred to as a vehicle and preferably designed as a motor vehicle, in particular as a passenger car, in its fully manufactured state has the temperature control device, by means of which at least the said partial region can be temperature controlled, i.e. cooled and / or heated. In particular, it is provided that in a method for operating the temperature control device, at least the partial region of the motor vehicle is temperature controlled, i.e. cooled and / or heated, by means of the temperature control device.For example, the sub-area is or comprises an interior of the motor vehicle, also referred to as a passenger cell or passenger compartment, in the interior of which persons such as the driver of the motor vehicle can be present while the motor vehicle is traveling. Alternatively or additionally, the sub-area can comprise, for example, an electrical energy storage device of the motor vehicle. Preferably, the electrical energy storage device, in or by means of which electrical energy can be or is stored, in particular electrochemically, is a high-voltage component whose electrical voltage, in particular electrical operating or nominal voltage, is preferably greater than 50 volts, in particular greater than 60 volts, and very preferably amounts to several hundred volts. The motor vehicle is thus, for example, a hybrid vehicle or an electric vehicle, in particular a battery electric vehicle (BEV).The motor vehicle has, for example, at least one electric machine by means of which the motor vehicle can be driven, in particular purely electrically. The electric machine is preferably a high-voltage component whose electrical voltage, in particular electrical operating or nominal voltage, is preferably greater than 50 volts, in particular greater than 60 volts, and very preferably amounts to several hundred volts. For example, the electric machine can be supplied with the electrical energy stored in the electrical energy store, whereby the electric machine can be operated in motor mode and thus as an electric motor by means of which the motor vehicle can be driven, in particular purely electrically.

[0006] The temperature control device has a refrigerant circuit, also simply referred to as a circuit, loop or refrigerant circuit, through which a refrigerant can flow and is flowed through in particular during the method. The refrigerant circuit has a refrigerant compressor. This means that the refrigerant compressor is arranged in the refrigerant circuit. The refrigerant compressor is also referred to as a compressor or condenser. The refrigerant is to be conveyed and compressed by means of the refrigerant compressor. In other words, the refrigerant compressor can convey and compress the refrigerant. Thus, for example, the method provides for the refrigerant to be conveyed and compressed by means of the refrigerant compressor. The refrigerant circuit also has a condenser for condensing the refrigerant. This means that the condenser is arranged in the refrigerant circuit.Thus, for example, the method provides for the refrigerant to be condensed, in particular in a targeted manner, by means of the condenser. This means that the refrigerant can be condensed, in particular in a targeted manner, by means of the condenser. By condensing the refrigerant, the refrigerant is to be cooled or is cooled. The refrigerant circuit also has at least one expansion valve for expanding the refrigerant. Thus, for example, the method provides for the refrigerant to be expanded by means of the expansion valve.

[0007] In order to be able to realize particularly advantageous and, in particular, particularly robust operation of the temperature control device, the temperature control device has a separation device arranged in the refrigerant circuit for the, in particular targeted, separation of a liquid phase of the refrigerant from a gaseous phase of the refrigerant. The separation device is provided in addition to the refrigerant compressor, in addition to the condenser, and in addition to the at least one expansion valve. A heating element for the, in particular targeted, heating of the refrigerant is integrated into the separation device. This is to be understood in particular that the heating element is a component of the separation device, wherein the separation device having the heating element is a structural unit manufactured, in particular considered on its own, and thus assembled.For example, the heating element is arranged in a housing of the separation device, which is also simply referred to as a separator. For example, a receiving space is delimited, in particular directly, by the housing, in particular by an inner circumferential surface of the housing, wherein the refrigerant can flow through or is flowed through the receiving space. This is to be understood in particular that at least the gaseous phase of the refrigerant can flow through or is flowed through the receiving space. It is preferably provided that the heating element is arranged in the receiving space so that the refrigerant can be effectively and efficiently warmed, i.e. heated, by means of the heating element, in particular on its way through the separation device, in particular through the receiving space.By integrating the heating element into the separation device, a particularly space-efficient arrangement of the heating element can be achieved, allowing for a particularly compact design of the temperature control device. Furthermore, the heating element makes it possible to specifically heat the refrigerant, which, for example, enables a particularly advantageous start-up of the initially deactivated temperature control device, also known as start-up or startup.In particular, the heating element makes it possible for the refrigerant to have an advantageously high temperature even before and / or upon starting the initially deactivated temperature control device, so that, for example, the temperature control device can be operated or transferred into operation right at the start of start-up or only a short time after start-up, wherein, in operation configured, for example, as a heat pump operation, the partial area can be particularly advantageously temperature-controlled, in particular heated, by means of the temperature control device. On the other hand, it is possible, for example, to avoid supplying the refrigerant compressor with wet steam or even liquid, so that undesirable damage to the refrigerant compressor can be avoided.

[0008] For example, the separation device can be used to separate the liquid phase from the gaseous phase of the refrigerant using gravity.

[0009] The refrigerant compressor has a low-pressure side, also referred to as the low-pressure region, and a high-pressure side, also referred to as the high-pressure region. The refrigerant compressor conveys the refrigerant towards itself on and via the low-pressure side, in particular in such a way that the refrigerant compressor draws in the refrigerant on its low-pressure side and thereby conveys it towards itself. The refrigerant compressor conveys the refrigerant from its low-pressure side to its high-pressure side, with the refrigerant compressor conveying the refrigerant away from itself on the high-pressure side. For example, the separation device is or comprises a container referred to as a vessel or buffer vessel, in which, for example, the separated liquid phase of the refrigerant can be at least temporarily accommodated.Thus, for example, the separation device, in particular the buffer vessel, can selectively store the refrigerant, in particular in the form of the liquid phase, or release it, i.e., make it available, in particular in gaseous form. The refrigerant received and thus stored in the separation device, in particular in the buffer vessel, does not flow through the refrigerant circuit when this refrigerant is not needed. If necessary, the separation device, in particular the vessel, can release the refrigerant stored within it, i.e., make it available, which then flows through the refrigerant circuit.

[0010] The separation device can, for example, be arranged on the high-pressure side of the refrigerant compressor, in which case the separation device is then arranged on the high-pressure side of the refrigerant compressor, downstream of the refrigerant compressor and downstream of the condenser, and very preferably upstream of the expansion valve. In this case, the separation device is also referred to, for example, as a collector or refrigerant collector. Furthermore, it is conceivable for the separation device to be arranged on the low-pressure side of the refrigerant compressor, in which case the separation device is then arranged on the low-pressure side of the refrigerant compressor, upstream of the refrigerant compressor and downstream of the expansion valve, and in particular downstream of the condenser. In this case, the separation device is also referred to, for example, as a separator or liquid separator.The separation device is in particular constructed or designed in such a way that phase separation takes place by gravity, by or during which the liquid phase is separated from the gaseous phase.

[0011] For example, the separation device has at least one outlet, also referred to as an output, through which the refrigerant can be discharged from the separation device. By positioning the outlet, it can be ensured or caused that the refrigerant exits the collector as a saturated liquid and the refrigerant exits the separator as a saturated vapor, thus exiting the separation device via the outlet.

[0012] In order to be able to realize particularly advantageous and particularly robust operation of the temperature control device, it is provided in one embodiment that the refrigerant circuit has a compressor train, also referred to as a compressor branch, which is also referred to as the first train or first branch. The compressor train can be or is flowed through by the refrigerant. The refrigerant circuit also has the refrigerant compressor, also referred to as a compressor or compressor, which is arranged in the compressor train. The refrigerant is to be conveyed and compressed by means of the refrigerant compressor. In other words, the refrigerant compressor can convey and compress the refrigerant. Thus, for example, the method provides for the refrigerant to be conveyed and compressed by means of the refrigerant compressor.

[0013] Preferably, the refrigerant circuit also comprises a condenser branch connected in fluidic series with the compressor branch and thus through which a first partial mass flow of the refrigerant flows, which is also referred to as a second branch or second branch. For example, the condenser branch branches off from the compressor branch, in particular at a first branch point. The expansion valve mentioned is arranged in the condenser branch as the first expansion valve, by means of which the first partial mass flow can be adjusted and expanded.

[0014] Thus, for example, the method provides for the first partial mass flow to be expanded by means of the first expansion valve. Thus, a plurality of different values ​​of the first partial mass flow can be set by means of the first expansion valve, so that the first partial mass flow can be varied. Furthermore, the condenser, by means of which the first partial mass flow can be condensed, in particular in a targeted manner, is arranged in the condenser branch. Thus, for example, the method provides for the first partial mass flow to be condensed, in particular in a targeted manner, by means of the condenser. By condensing the first partial mass flow, the first partial mass flow is or is to be cooled.

[0015] The coolant circuit preferably also has a bypass branch which is connected in fluidic series with the compressor branch and in fluidic parallel with the condenser branch and can thus be flowed through by a second partial mass flow of the refrigerant. The bypass branch is also referred to as a third branch or third branch. Thus, for example, the method provides for the second partial mass flow to flow through the bypass branch. For example, the bypass branch branches off from the compressor branch, in particular at a second branching point. The branching points can coincide and thus be formed by a single overall branching point or be located at a single overall branching point, or the branching points can be spaced from one another, in particular in the flow direction of the refrigerant flowing through the refrigerant circuit.In particular, it is provided for example in the method that the second partial mass flow flows through the bypass branch. In the bypass branch there is a second expansion valve, which is provided in particular in addition to the first expansion valve and by means of which the second partial mass flow can be adjusted and expanded. Thus, it is provided in particular in the method that the second partial mass flow is expanded by means of the second expansion valve. The feature that the second partial mass flow can be adjusted by means of the second expansion valve is to be understood in particular that a plurality of different values ​​of the second partial mass flow can be adjusted by means of the second expansion valve, whereby the second partial mass flow can be varied, i.e. changed.The first partial mass flow or the second partial mass flow can be adjusted by the respective first or second expansion valve, in particular by adjusting a respective flow cross-section of the respective expansion valve through which the first or second partial mass flow can flow, i.e. different values ​​of the respective flow cross-section can be adjusted.

[0016] The first partial mass flow flows through or through the first expansion valve, and the second partial mass flow flows through or through the second expansion valve. The refrigerant compressor and thus, for example, the compressor train, i.e. at least a part of the compressor train, can be or are flowed through or through by a compressor flow formed by the refrigerant, which is a mass flow of the refrigerant. The compressor flow comprises at least the first partial mass flow and the second partial mass flow and is therefore formed at least by the first partial mass flow and by the second partial mass flow. In addition, the condenser can be or is flowed through or through by the second partial mass flow.The condenser is, for example, a heat exchanger which, for example, can be operated or is operated or functions as the condenser, at least in the aforementioned operation of the temperature control device, which is designed, for example, as a heat pump operation. For example, a fluid provided in addition to the coolant can flow through and / or around the condenser. For example, heat can be transferred from the coolant to the fluid via the condenser, as a result of which the coolant is cooled and the fluid is heated, particularly in the aforementioned operation. Heat contained in the coolant can thus be used to heat the fluid. The fluid can, for example, be supplied to the sub-region in order to heat the sub-region by means of the fluid, in particular by means of the heat that has been transferred from the coolant to or to the fluid via the condenser, and thus to temperature it.More generally, the sub-region can, for example, be tempered, in particular heated, by means of the fluid, in particular by means of the heat contained in the fluid, which has been transferred from the coolant to or onto the fluid via the condenser. For example, the fluid is a gas, in particular air, which is or can be introduced into the sub-region, in particular into the aforementioned interior space, in order to thereby temper, in particular heat, the sub-region, in particular the interior space, by means of the fluid. Furthermore, it is conceivable for the fluid to be a liquid. For example, the electrical energy store can be tempered, in particular heated, by means of the fluid. For this purpose, the electrical energy store is supplied with the fluid, for example. In particular, the aforementioned operation is, for example, a heat pump operation.

[0017] The heat that has been transferred from the refrigerant to or to the fluid via the condenser can, for example, be transferred from the fluid to or to the electrical energy storage device in order to heat the electrical energy storage device and thus control its temperature. The heat mentioned, which is transferable or is transferred from the refrigerant to or to the fluid via the condenser, originates, for example, at least predominantly or exclusively from the refrigerant compressor or is at least predominantly or exclusively caused by the refrigerant compressor or fed into the refrigerant, in particular by the refrigerant compressor compressing the refrigerant and thereby heating it. The refrigerant compressor can thus be used as a heat source to heat the refrigerant and, in particular via the condenser, for example the fluid and subsequently to heat the sub-region.

[0018] Furthermore, it is provided, for example, that the bypass branch and the condenser branch are brought together at, in particular precisely, a mixing point and are thereby fluidically connected to one another. At the mixing point, the first partial mass flow and the second partial mass flow are or can be brought together to form a total mass flow, and at the mixing point, the first partial mass flow and the second partial mass flow are or can be mixed or blended with one another in that the first partial mass flow and the second partial mass flow are or can be brought together to form the total mass flow at the mixing point. Thus, the compressor flow flowing through the refrigerant compressor comprises at least or exclusively the total mass flow.In particular, it is conceivable that in a first operating state of the temperature control device, the compressor flow exclusively comprises the total mass flow, thus exclusively the first partial mass flow and the second partial mass flow, and is thus formed exclusively by the total mass flow. In a second operating state of the temperature control device, the compressor flow comprises, for example, in particular exclusively, the total mass flow and at least or exactly one further partial mass flow of the refrigerant, so that in the second operating state, the compressor flow is formed, in particular exclusively, by the first partial mass flow and the second partial mass flow and the at least or exactly one further partial mass flow of the refrigerant.Because the first partial mass flow and the second partial mass flow are brought together at the mixing point and are or can be mixed with one another, the first partial mass flow and the second partial mass flow form or result in the total mass flow, which can, for example, be introduced into the compressor train and thus flow in and subsequently flow through the compressor train and, in particular, the refrigerant compressor. Because the first partial mass flow and the second partial mass flow result in or form the total mass flow because the first partial mass flow and the second partial mass flow are brought together and thereby mixed with one another, the first partial mass flow and the second partial mass flow, each considered individually, are smaller than the total mass flow and the compressor flow.In addition, the further partial mass flow considered on its own is lower than the compressor flow and, for example, than the total mass flow.

[0019] For example, it is provided that, for example, at the first branching point, the first partial mass flow branches off from the compressor flow or from a further mass flow of the refrigerant branched off from the compressor flow. Furthermore, it is provided, for example, that, in particular, at the second branching point, the second partial mass flow branches off from the compressor flow or from the further mass flow. If the branching points coincide, it is conceivable that the compressor flow or the further mass flow is branched, i.e., divided, at the overall branching point into the first partial mass flow and the second partial mass flow.

[0020] In the method for operating the temperature control device, a first pressure and a first temperature of the refrigerant, in particular of the compressor flow flowing through the refrigerant compressor, are determined in the compressor train upstream of the refrigerant compressor and downstream of the mixing point, for example by means of an electronic computing device, in particular of the temperature control device, very particularly of the motor vehicle. The first pressure of the refrigerant, in particular of the compressor flow, is understood to mean a pressure of the refrigerant, in particular of the compressor flow, wherein the first pressure prevails at a first pressure point arranged in the compressor train upstream of the refrigerant compressor and downstream of the mixing point.The first temperature of the refrigerant, in particular of the compressor flow, is understood to mean a temperature of the refrigerant, in particular of the compressor flow, wherein the first temperature prevails at a first temperature point located in the compressor train upstream of the refrigerant compressor and downstream of the mixing point. For example, the first pressure point and the first temperature point coincide.

[0021] By means of the electronic computing device, a second pressure and a second temperature of the refrigerant are determined downstream of the refrigerant compressor, upstream of the condenser, and upstream of the expansion valves. The second refrigerant pressure is to be understood as a refrigerant pressure, wherein the second pressure prevails at a second pressure point arranged downstream of the refrigerant compressor and upstream of the condenser and upstream of the expansion valves, wherein the second pressure point is arranged, for example, in the compressor train or in the bypass train or in the condenser train. Thus, for example, the second pressure is a second pressure of the compressor stream flowing through the refrigerant compressor, which has the second pressure downstream of the refrigerant compressor and upstream of the condenser and upstream of the expansion valves, in particular in the compressor train and very particularly upstream of the branch points.When reference is made above and below to the expansion valves, this refers, unless otherwise stated, to the first expansion valve and the second expansion valve. The second temperature of the refrigerant is understood to mean a temperature of the refrigerant, wherein the second temperature prevails at a second temperature point located downstream of the refrigerant compressor, upstream of the condenser, and upstream of the expansion valves, wherein the second temperature point is located in the compressor line, in the bypass line, or in the condenser line. In particular, it is conceivable that the second pressure point and the second temperature point coincide.Thus, for example, the second temperature is a second temperature of the compressor flow flowing through the refrigerant compressor, which has the second temperature downstream of the refrigerant compressor and upstream of the condenser and upstream of the expansion valves, in particular in the compressor train and very particularly upstream of the branch points.

[0022] By means of the electronic computing device, a third pressure and a third temperature of the refrigerant, in particular of the first partial mass flow, are determined in the condenser branch downstream of the condenser and upstream of the first expansion valve. The third pressure of the refrigerant, in particular of the first partial mass flow, is to be understood as a pressure of the refrigerant, in particular of the first partial mass flow, wherein the third pressure prevails at a third pressure point arranged in the condenser branch downstream of the condenser and upstream of the first expansion valve. The third temperature of the refrigerant, in particular of the first partial mass flow, is to be understood as a temperature of the refrigerant, in particular of the first partial mass flow, wherein the third temperature prevails at a third temperature point arranged in the condenser branch downstream of the condenser and upstream of the first expansion valve.The third pressure point and the third temperature point may coincide.

[0023] As previously described, the compressor flow can flow through the refrigerant compressor, so that, for example, in the method, the compressor flow flows through the refrigerant compressor and thus, for example, through at least part of the compressor train. The pressures and temperatures are determined using the electronic computing device, which will be explained in more detail below.

[0024] In the method, the expansion valves are controlled by the electronic computer depending on the determined temperatures and the determined pressures, whereby the first partial mass flow and the second partial mass flow are adjusted depending on the determined temperatures and the determined pressures. When reference is made to partial mass flows above and below, this refers to the first partial mass flow and the second partial mass flow, unless otherwise stated.This means that by means of the electronic computing device, the partial mass flows are adjusted, i.e., in particular, varied, via the expansion valves, i.e., by controlling the expansion valves, depending on the determined pressures and depending on the determined temperatures. For example, by adjusting, i.e., in particular, varying, the flow cross-sections of the expansion valves by controlling the expansion valves. This makes it particularly advantageous to set a ratio, also referred to as a mixing ratio, between the partial mass flows, in particular a ratio of the first partial mass flow to the second partial mass flow, so that robust operation of the temperature control device and, consequently, effective and efficient temperature control can be achieved.In particular, by adjusting the first partial mass flow and the second partial mass flow, and thus by adjusting the mixing ratio, it is possible to prevent the refrigerant compressor from being supplied with wet vapor or even liquid. In other words, for example, it is possible to prevent the compressor flow flowing through the compressor train and comprising at least the first partial mass flow and the second partial mass flow, which results from the mixing of at least the first partial mass flow with the second partial mass flow, from containing wet vapor or even liquid, thus preventing undesirable damage to the temperature control device.Furthermore, it is possible to achieve particularly advantageous temperature control of the sub-area without having to install an electric flow heater in the refrigerant circuit or in an additional temperature control circuit intended for temperature control of the sub-area and through which the fluid can flow, for example. Furthermore, a heat exchanger arranged in the refrigerant circuit and, for example, in the temperature control circuit, also referred to as a chiller and operable or operated as an evaporator, can be dispensed with, so that the number of parts and thus the weight and cost of the temperature control device can be kept particularly low.At the same time, it is possible to advantageously adjust the partial mass flows and thus the mixing ratio in such a way that the total mass flow has a particularly advantageous state, in particular state of aggregation, in particular in such a way that, for example, the enthalpy of the total mass flow lies to the right of the dew line of the refrigerant formed, for example, as R1234yf, in particular in a phase diagram of the refrigerant, wherein, for example, the enthalpy, in particular the specific enthalpy, is plotted on the abscissa of the phase diagram, and wherein the pressure of the refrigerant is plotted, in particular logarithmically, on the ordinate of the phase diagram.

[0025] The heating element is a heat source integrated into the separation device. The integration of the heating shaft into the separation device is advantageous in that, in addition to a refrigerant flow, a particularly high quantity of refrigerant can also be provided for heating at an outlet of the separation device, via which the separation device can, for example, provide the gaseous phase of the refrigerant. For example, by positioning the heat source at the outlet (also referred to as the outlet), it can also be ensured that the refrigerant compressor is supplied exclusively with superheated vapor, i.e., that only superheated vapor is present at the inlet of the refrigerant compressor.This allows the refrigerant compressor to be protected, and the initially deactivated temperature control device can be started up particularly quickly and operated in the aforementioned mode, in particular heat pump mode, shortly after its start-up or directly upon start-up.

[0026] In order to be able to heat the refrigerant particularly effectively and efficiently by means of the separation device, that is to say by means of the heating element of the separation device, and thus to start the temperature control device particularly advantageously and subsequently operate it robustly, it is provided in a further embodiment of the invention that the separation device and thus the heating element are arranged, in particular in the flow direction of the refrigerant flowing through the refrigerant circuit, upstream of the refrigerant compressor, downstream of the first expansion valve, downstream of the condenser and downstream of the second expansion valve, so that, for example, the separation device can be flowed through by both the first partial mass flow and the second partial mass flow.Thus, the separation device and thus the heating element are preferably arranged on a low-pressure side of the refrigerant compressor, also referred to as the low-pressure area, which sucks in the refrigerant via its low-pressure side or conveys it towards itself and then conveys the refrigerant away from itself via its high-pressure side.

[0027] In order to be able to create a particularly compact and thus robust and efficient design of the tempering device, it is provided in a further embodiment of the invention that the separation device is arranged at the mixing point.

[0028] It has also been shown to be particularly advantageous if the separation device is arranged in the compressor train upstream of the refrigerant compressor and downstream of the mixing point, whereby the refrigerant is heated particularly advantageously and as a result the temperature control device can be started and subsequently operated particularly advantageously.

[0029] In order to be able to start the temperature control device particularly advantageously and subsequently operate it particularly advantageously and robustly, it has proven particularly advantageous if the separation device is arranged in the condenser train downstream of the condenser, downstream of the first expansion valve and upstream of the mixing point.

[0030] A further embodiment is characterized in that the separation device is arranged in the bypass line downstream of the second expansion valve and upstream of the mixing point, whereby a particularly advantageous and robust operation of the temperature control device can be realized.

[0031] In order to heat the refrigerant effectively, efficiently, and particularly as needed, and consequently to be able to start and operate the temperature control device particularly advantageously and robustly, a further embodiment of the invention provides for the heating element to be designed as an electrical heating element. This means that the heating element can be operated electrically. In order to operate the heating element electrically, the heating element can be supplied or can be supplied with electrical energy. By electrically operating the heating element, the refrigerant can be heated and thus electrically heated by means of the heating element using the electrical energy with which the heating element is supplied or can be supplied, whereby the refrigerant can be heated effectively and efficiently.

[0032] Finally, to achieve particularly advantageous operation, it has proven particularly advantageous if the separation device has a collection area for at least temporarily collecting the separated liquid phase. For example, the collection area is formed by the aforementioned vessel or, in particular, directly bounded by it.

[0033] A second aspect of the invention relates to a method for operating a temperature control device according to the first aspect of the invention. Advantages and advantageous embodiments of the first aspect of the invention are to be regarded as advantages and advantageous embodiments of the second aspect of the invention, and vice versa.

[0034] A third aspect of the invention relates to a motor vehicle, also simply referred to as a vehicle and preferably designed as a motor vehicle, in particular as a passenger car, which has at least one temperature control device according to the first aspect of the invention.

[0035] Further details of the invention will become apparent from the following description of a preferred embodiment with the accompanying drawings. In the drawings: Fig. 1 a schematic representation of a temperature control device for tempering a part of a motor vehicle; Fig. 2 a phase diagram of a refrigerant flowing through a refrigerant circuit of the temperature control device in a method for operating the temperature control device; and Fig. 3 a schematic sectional view of a separation device of the temperature control device arranged in the refrigerant circuit.

[0036] In the figures, identical or functionally identical elements are provided with the same reference numerals.

[0037] Fig. 1 shows a schematic representation of a temperature control device 6 of a motor vehicle, also simply referred to as a vehicle and preferably designed as a motor vehicle, in particular as a passenger car. In particular, a method for operating the temperature control device 6 is described with reference to the figure. By means of the temperature control device 6, at least a partial area of ​​the motor vehicle can be temperature-controlled, i.e., heated or cooled. In particular, the partial area can be heated. For example, the partial area is or comprises an interior of the motor vehicle, also referred to as a passenger cell or passenger compartment, the structure of which, for example, is designed as a self-supporting body, forms or delimits the interior. Thus, for example, the interior can be temperature-controlled, in particular heated, by means of the temperature control device 6.For this purpose, the temperature control device 6 has a refrigerant circuit 7 through which a refrigerant can flow, which circuit is flowed through by the refrigerant during the method and thus during operation of the temperature control device 6, which is operated according to the method.

[0038] The refrigerant circuit 7 has a compressor train 9 through which the refrigerant can flow. A refrigerant compressor 11 is arranged in the compressor train 9, by means of which the refrigerant can be conveyed and compressed. In the aforementioned operation and thus in the method, for example, the refrigerant is conveyed and compressed by means of the refrigerant compressor 11. In particular, the refrigerant compressor 11 and thus at least a portion of the compressor train 9 can be flowed through by a compressor flow formed by the refrigerant, wherein the compressor flow is a mass flow of the refrigerant flowing through the refrigerant compressor 11. For example, the compressor flow is or comprises at least or exclusively a total mass flow of the refrigerant embodied as a mass flow of the refrigerant, which will be explained in more detail below.

[0039] The refrigerant circuit 7 has a condenser branch 12 which is connected in series with the compressor branch 9 in terms of flow technology and, in this case, branches off from the compressor branch 9 at a branch point A, and through which a first partial mass flow of the refrigerant can flow. A condenser 14, also referred to as a condenser, is arranged in the condenser branch 12, by means of which the first partial mass flow, i.e. the refrigerant flowing through the condenser branch 12, can be or is condensed, i.e. liquefied. Furthermore, a first expansion valve 15 is arranged in the condenser branch 12 downstream of the condenser 14, by means of which the first partial mass flow can be adjusted. Furthermore, the first partial mass flow, i.e. the refrigerant flowing through the condenser branch 12, can be or is expanded by means of the expansion valve 15.

[0040] The refrigerant circuit 7 also has a bypass line 16, which is connected fluidically parallel to the condenser line 12 and fluidically serial to the compressor line 9 and, in this case, branches off from the compressor line 9 at branch point A, allowing a second partial mass flow of the refrigerant to flow through it. Since both the bypass line 16 and the condenser line 12 branch off from the compressor line 9 at branch point A, branch point A is a complete branch point.

[0041] In the bypass line 16, a second expansion valve 18 is provided in addition to the expansion valve 15, by means of which the second partial mass flow can be adjusted. Furthermore, the second partial mass flow, thus the refrigerant flowing through the bypass line 16, is or is expanded by means of the expansion valve 18. Preferably, it is provided that, during the method, evaporation of the refrigerant by means of an evaporator is avoided in the compressor line 9, in the condenser line 12 and in the bypass line 16, in particular in the entire refrigerant circuit 7. The compressor line 9, the condenser line 12 and the bypass line 16 are also referred to as lines. In the exemplary embodiment shown in the figures, the lines are free of an evaporator for the targeted evaporation of the refrigerant.

[0042] The condenser branch 12 and the bypass branch 16 are brought together at, in particular precisely, a mixing point M of the refrigerant circuit 7, so that at the mixing point M the first partial mass flow and the second partial mass flow can be brought together to form the total mass flow and can thereby be mixed with one another, and thus brought together in the method and can thereby be mixed or blended with one another. The total mass flow can be introduced into the compressor branch 9, in particular from the mixing point M, and can thus flow in and subsequently flow through the compressor branch 9 and thus the refrigerant compressor 11. In other words, the total mass flow can be fed to the refrigerant compressor 11, in particular starting from the mixing point M, and can thus flow through the refrigerant compressor 11. The compressor flow is thus or comprises at least the total mass flow.In other words, it is conceivable that the compressor flow, at least in a first operating state of the temperature control device 6, exclusively comprises the total mass flow and is thus formed exclusively by the total mass flow. Furthermore, it is conceivable that, in particular in a second operating state of the temperature control device 6, the compressor flow comprises the total mass flow and at least or exactly one further partial mass flow of the refrigerant and is thus formed by the total mass flow and by the further partial mass flow of the refrigerant and, in particular, exclusively comprises the total mass flow and the further partial mass flow.

[0043] By means of a Fig. 1, a first pressure and a first temperature of the refrigerant, in particular of the compressor flow, in the compressor train 9 upstream of the refrigerant compressor 11 and downstream of the mixing point M are determined. Fig. In the embodiment shown in Figure 1, a first sensor device S1 is provided, by means of which the first pressure prevailing in the compressor line 9 upstream of the refrigerant compressor 11 and downstream of the mixing point M and the first temperature of the refrigerant, in particular of the compressor flow, prevailing in the compressor line 9 upstream of the refrigerant compressor 11 and downstream of the mixing point M are measured. The sensor device S1 provides, for example, a first signal characterizing the first temperature and the first pressure, which is received by the electronic computing device 19, whereby the electronic computing device 19 determines the first temperature and the first pressure. Fig. 1, a first point is designated by 1, which is also referred to as the first location. The first point 1 is arranged in the compressor train 9 downstream of the mixing point M and upstream of the refrigerant compressor 11, wherein, for example, the sensor device S1 measures the first pressure and the first temperature in or at the first point 1. In other words, for example, the first pressure and the first temperature of the refrigerant prevail in the compressor train 9 at point 1.

[0044] By means of the electronic computing device 19, a second pressure and a second temperature of the refrigerant, in particular of the compressor flow, are determined downstream of the refrigerant compressor 11, upstream of the condenser 14 and upstream of the expansion valves 15 and 18. In the Fig. In the embodiment shown in Figure 1, a second sensor device S2 is provided, by means of which the second pressure of the refrigerant prevailing downstream of the refrigerant compressor 11, upstream of the condenser 14, and upstream of the expansion valves 15 and 18, and the second temperature of the refrigerant prevailing downstream of the refrigerant compressor 11, upstream of the condenser 14, and upstream of the expansion valves 15 and 18 are detected. The sensor device S2 provides, for example, a second signal that characterizes the second temperature and the second pressure. For example, the electronic computing device 19 receives the second signal, whereby the electronic computing device 19 determines the second pressure and the second temperature. In Fig. 1, a second point is designated by 2, wherein the second point is also referred to as the second location. It can be seen that the first point 1 is arranged downstream of the mixing point M and upstream of the refrigerant compressor 11 in the compressor train 9. The second point 2 is arranged downstream of the refrigerant compressor 11, upstream of the condenser 14 and upstream of the expansion valves 15 and 18, wherein, for example, the second point 2 can be arranged at a branch point A or coincide with the branch point A. The condenser train 12 and the bypass train 16 branch off from the compressor train 9 at the branch point A. For example, the second pressure and the second temperature prevail at or in the second point 2, wherein, for example, the second sensor device S2 measures the second pressure and the second temperature in or at the second point 2.

[0045] By means of the electronic computing device 19, a third pressure and a third temperature of the refrigerant, in particular of the first partial mass flow, are determined in the condenser branch 12 downstream of the condenser 14 and upstream of the first expansion valve 15, which in the case of Fig. 1 is arranged in the condenser train 12 downstream of the condenser 14 and upstream of the mixing point M. In the embodiment shown in Fig. In the embodiment shown in Figure 1, a third sensor device S3 is provided, by means of which the third pressure of the refrigerant prevailing in the condenser branch 12 downstream of the condenser 14 and upstream of the first expansion valve 15 and the third temperature of the refrigerant prevailing in the condenser branch 12 downstream of the condenser 14 and upstream of the expansion valve 15 are detected. For example, the third sensor device S3 provides a third signal that characterizes the third temperature and the third pressure. The electronic computing device 19 receives, for example, the third signal, whereby the electronic computing device 19 determines the third temperature and the third pressure.

[0046] By means of the electronic computing device 19, the expansion valves 15 and 18 are controlled as a function of the determined temperatures and as a function of the determined pressures, whereby the first partial mass flow and the second partial mass flow are adjusted as a function of the determined temperatures and as a function of the determined pressures. This sets a mixing ratio, also referred to as a mixing ratio, according to which the first partial mass flow and the second partial mass flow are mixed or blended with one another, resulting in the total mass flow. In particular, the mixing ratio is or describes a quotient, also referred to as a mixing quotient, wherein the mixing quotient has, for example, the first partial mass flow in its numerator, and wherein the mixing quotient has, for example, the second partial mass flow in its denominator.The first partial mass flow is denoted, for example, by m1, and the second partial mass flow is denoted, for example, by m2. The mixing ratio is denoted, for example, by Φ. Thus, for example, the following applies: Φ=m1m2.

[0047] By controlling the expansion valve 15, for example, a first flow cross-section of the first expansion valve 15 through which the first partial mass flow can flow can be adjusted, i.e., changed. For example, the expansion valve 15 has a first, in particular electrically operable, actuator, by means of which the first flow cross-section can be adjusted. For example, the expansion valve 18 has a second flow cross-section through which the second partial mass flow can flow, which can be adjusted, i.e., changed, by controlling the expansion valve 18. For example, the expansion valve 18 has a second actuator, in particular electrically operable, by means of which the second flow cross-section can be adjusted.The electronic computing device 19, for example, controls the actuators as a function of the determined pressures and as a function of the determined temperatures in order to adjust the flow cross sections and consequently the partial mass flows and thus the mixing ratio Φ.

[0048] In Fig. 1, a third point is designated by 3, wherein the third point 3 is also referred to as the third location. It can be seen that the third point 3 is arranged in the condenser branch 12 downstream of the condenser 14 and upstream of the expansion valve 15. For example, the third temperature and the third pressure prevail at or in the third point 3. For example, the third sensor device S3 measures the third pressure and the third temperature at or in the third point 3. Furthermore, in Fig. 1, a fourth point is designated by 4, whereby the fourth point is also referred to as the fourth point or is a fourth point. It can be seen that the fourth point, hence the fourth point 4, is located in the condenser branch 12 and downstream of the expansion valve 15 and upstream of the mixing point M. Furthermore, in Fig. 1, a fifth point is designated by 5, wherein the fifth point 5 is also referred to as a fifth location or is designed as a fifth location. It can be seen that the fifth point 5 is located in the bypass line 16 downstream of the expansion valve 18 and upstream of the mixing point M.

[0049] The refrigerant circuit 7 can be flowed through by the refrigerant in a flow direction also referred to as the operating direction. It is particularly provided that, during the aforementioned operation of the temperature control device 6, the refrigerant flows through the refrigerant circuit 7 in the operating direction. The operating direction is illustrated by arrows 8. Furthermore, an arrow 10 illustrates the compressor flow, an arrow 13 illustrates the first partial mass flow, and an arrow 17 illustrates the second partial mass flow.

[0050] In order to be able to realize particularly advantageous, in particular particularly robust, operation of the temperature control device 6, the temperature control device 6 has a separation device 32, which is arranged in the refrigerant circuit 7. The separation device 32 is provided in addition to the expansion valves 15 and 18, in addition to the refrigerant compressor 11 and in addition to the condenser 14. By means of the separation device 32, a liquid phase of the refrigerant can be or is separated from a gaseous phase of the refrigerant. A heating element 33, by means of which the refrigerant can be heated in a targeted manner, is integrated into the separation device 32. In the exemplary embodiment shown in the figures, the heating element 33 is an electrical heating element, by means of which the refrigerant can be or is heated using electrical energy with which the heating element 33 is or can be supplied.With regard to the separation device 32, in particular with regard to a positioning or arrangement of the separation device 32 in the refrigerant circuit 7, . Fig. 1 illustrates three possible variants V1, V2, and V3. In all three variants V1, V2, and V3, the separation device 32 and thus the heating element 33 are arranged, particularly with respect to the operating direction, upstream of the refrigerant compressor 11, downstream of the first expansion valve 15, downstream of the condenser 14, and downstream of the second expansion valve 18, and thus on a low-pressure side of the refrigerant compressor 11. In variant V1, the separation device 32 is arranged in the compressor train 9 upstream of the refrigerant compressor 11 and downstream of the mixing point M. In variant V1, the separation device 32 is a so-called separator.

[0051] In variant V2, the separation device 32 is arranged in the condenser branch 12 downstream of the condenser 14, downstream of the first expansion valve 15 and upstream of the mixing point M. In variant V2, the separation device 32 is a so-called separator. In variant V3, the separation device 32 is arranged in the condenser branch 12 downstream of the condenser 14, upstream of the first expansion valve 15 and upstream of the mixing point M. In variant V3, the separation device 32 is a so-called collector.

[0052] Fig. Figure 3 shows the separating device 32 designed as a collector. The separating device 32 has a housing 34, wherein a receiving space 36 is delimited, in particular directly, by the housing 34, in particular by an inner circumferential surface 35 of the housing 34. The liquid phase of the refrigerant separated from or from the gaseous phase by the separating device 32 is in Fig. 3 designated by 37. The separation device 32, in particular the housing 34, which is also referred to as a vessel or buffer vessel, has an inlet 38, which is arranged in particular at an inlet 39 of the separation device 32. The refrigerant can be introduced into the separation device 32, in particular into the receiving space 36, via the inlet 38. The separation device 32, in particular the housing 34, also has an outlet 40, which is also referred to as an output or outlet and is arranged in particular at an outlet 41, also referred to as an outlet, of the separation device 32 or forms the outlet 41. The refrigerant can be discharged from the separation device 32, in particular from the receiving space 36, via the outlet 40, in particular via the outlet 41, in particular in liquid form or in the liquid state of the refrigerant.In the present case, the outlet 40 is or comprises a drain line 42, by means of which or via which the refrigerant, in particular in liquid form, can be discharged from the receiving space 36 and thus from the separation device 32, so that, for example, the liquid phase 37 of the refrigerant can be discharged from the separation device 32 via the drain line 42, the hot phase via the outlet 40 and the outlet 41. It can be seen that the line element 42 is immersed in the liquid phase 37.

[0053] Out of Fig. 3 shows that the heating element 33 is arranged at the outlet 41 and, in particular, at the outlet 40, in particular the line element 42, so that, for example, the refrigerant can be heated or is heated by the heating element 33 on its way through the line element 42. As a result, the refrigerant at the outlet 41 can have a particularly advantageously high temperature.

[0054] Particularly schematically shown in Fig. 3 shows an electronic processing unit 43 assigned to the electric heating element 33, by means of which the heating element 33 can be controlled and thus operated, in particular controlled or regulated. By controlling and operating the heating element 33 in this way, a temperature of the coolant that is or can be achieved by the heating element 33 can be adjusted, i.e., changed. It can be seen that, for example, the electronic processing unit 43 is also integrated into the separation device 32. Furthermore, it can be seen that the heating element 33 and, in the present case, for example, also the processing unit 43 are arranged in the housing 34, in particular in the receiving space 36.

[0055] The separation device 32, designed as a collective separator, has a collection area 44, which is delimited by the housing 34, in particular by the inner circumferential surface 35, in particular directly. In the collection area 44, the separated liquid phase 37 can be collected at least temporarily. For example, the separated liquid phase 37 can be discharged from the receiving space 36 via the outlet 40. In this case, the expansion valve 15 is connected, for example, to the separation device 32 and upstream of the refrigerant compressor 11, so that the liquid phase 37 discharged from the collection area 44 and thus from the receiving space 36 via the outlet 40 can be expanded by means of the expansion valve 15. Thus, for example, the Fig. 3 illustrated separating device 32 is used in particular in variant V3.

[0056] Fig. 2 shows a phase diagram of the refrigerant, for example, formed as R1234yf, where the Fig. 2 illustrates the operation of the temperature control device 6. As usual, the abscissa 20 of the phase diagram shows the enthalpy of the refrigerant, in particular the specific enthalpy, in particular in kilojoules per kilogram. As usual, the pressure of the refrigerant, in particular in bar, is shown or indicated logarithmically on the ordinate 21 of the phase diagram. The dew point of the refrigerant in the phase diagram is designated by 22. Points 1, 2, 3, 4 and 4 are entered in the phase diagram, so that from the Fig. 2, the respective enthalpy of the refrigerant can be seen at points 1, 2, 3, 4 and 5. In particular, it can be seen that the enthalpy of the refrigerant is the same at points 1, 4 and 5, and the enthalpy of the refrigerant is the same at points 2 and 3. In Fig. In Figure 2, an arrow 23 illustrates a change in state of the refrigerant from point 1 to point 2, and an arrow 24 illustrates a change in state of the refrigerant from point 2 to point 5. An arrow 25 illustrates a change in state of the refrigerant from point 2 to point 3, and an arrow 26 illustrates a change in state of the refrigerant from point 3 to point 4. The respective change in state is to be understood as a respective change in the thermodynamic state of the refrigerant. It can be seen that a first thermodynamic cycle, designed as a first triangular process, takes place via points 1, 2, 3, and 4, i.e., via the compressor train 9 and the condenser train 12, and a second thermodynamic cycle, designed as a second triangular process, takes place via points 1, 2, and 5, i.e., via the compressor train and the bypass train 16.The triangular processes, also referred to simply as processes, are parallel, although none of the triangular processes is self-contained. It is desirable that point 1 be related to the point shown in . Fig. 2, the phase diagram shown is stable to the right of the dew line 22. In other words, it is desirable that the first partial mass flow and the second partial mass flow and thus the mixing ratio or, in particular in the first switching state, a total mixing ratio, according to which, in particular in the first switching state, the first partial mass flow and the second partial mass flow are mixed or blended with each other and are adjusted by means of the expansion valves 15 and 18 such that the enthalpy of the refrigerant at or in the point 1 relative to the in Fig. 2 shown phase diagram lies safely or stably to the right of the dew line 22.

[0057] By adjusting the first partial mass flow and the second partial mass flow, a total mass flow can be adjusted from the partial mass flows, i.e. from the first partial mass flow and the second partial mass flow. Thus, it is desirable that the first partial mass flow and the second partial mass flow and thus the mixing ratio and very preferably the total mixing ratio, also referred to as the total mixing ratio, are adjusted by means of the expansion valves 15 and 18 such that the enthalpy of the refrigerant at or in point 1 relative to the Fig. 2 is reliably or stably positioned to the right of the dew line 22. This ensures that the compressor flow is at least predominantly, in particular exclusively, superheated steam. In other words, this prevents the refrigerant compressor 11 from being flowed through by wet steam or a liquid, which could lead to damage to the refrigerant compressor 11. Operating the temperature control device 6 in such a way that the enthalpy of the refrigerant at or in the point 1 relative to the Fig. 2 shown phase diagram lies safely to the right of the dew line 22, is also called stabilizing stabilization.

[0058] Out of Fig. 2, it can be seen that the refrigerant has a first enthalpy at or in the first point 1, a second enthalpy at or in the second point, a third enthalpy at or in the third point 3, a fourth enthalpy at or in the fourth point 4, and a fifth enthalpy at or in the fifth point 5. The fourth enthalpy corresponds to the third enthalpy, and the fifth enthalpy corresponds to the second enthalpy. Furthermore, for example, the refrigerant has the same pressure, in particular the same first pressure, at or in points 1, 4, and 5. Fig. In Figure 2, a sixth point 31 illustrates the enthalpy of the refrigerant corresponding to the first pressure and located on the dew line 22 of the refrigerant. The enthalpy of the refrigerant corresponding to the first pressure and located on the dew line 22 of the refrigerant, illustrated by point 31, is also referred to as the dew line enthalpy. List of reference symbols 1 point 2 points 3 point 4 points 5 points 6 Tempering device 7 Refrigerant circuit 8 Arrow 9 Compressor train 10 Arrow 11 Refrigerant compressors 12 capacitor train 13 Arrow 14 Capacitor 15 first expansion valve 16 Bypass line 17 Arrow 18 second expansion valve 19 electronic computing device 20 Abscissa 21 Ordinates 22 dew line 23 Arrow 24 Arrow 25 Arrow 26 Arrow 31 points 32 Separation device 33 Heating element 34 housings 35 inner circumferential surface 36 Recording Room 37 liquid phase 38 inlet 39 Entrance 40 Process 41 Exit 42 Line element 43 electronic computing unit 44 Collection area A junction point M mixing point S1 sensor device S2 sensor device S3 sensor device V1 variant V2 variant V3 variant QUOTES CONTAINED IN THE DESCRIPTION

[0000] This list of documents submitted by the applicant was generated automatically and is included solely for the convenience of the reader. This list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions. Cited patent literature

[0000] JP 5861 495 B2

[0002] EP 2 265 453 B1

[0002] DE 603 ​​20 060 T2

[0002]

Claims

[1] Tempering device (6) for tempering at least a partial area of ​​a motor vehicle, comprising: - a refrigerant circuit (7) through which a refrigerant can flow, which comprises: ◯ a refrigerant compressor (11) by means of which the refrigerant is to be conveyed and compressed; ◯ a condenser (14) for condensing the refrigerant; and ◯ at least one expansion valve (15) for expanding the refrigerant; and - a separation device (32) arranged in the refrigerant circuit (7) for separating a liquid phase (37) of the refrigerant from a gaseous phase of the refrigerant, wherein a heating element (33) for heating the refrigerant is integrated into the separation device (32). [2] Tempering device (6) according to claim 1, characterized by that the refrigerant circuit (7) has: ◯ a compressor train (9) through which the refrigerant flows, in which the refrigerant compressor (11) is arranged, by means of which the refrigerant is to be conveyed and compressed; ◯ a condenser branch (12) connected in series with the compressor branch (9) and through which a first partial mass flow of the refrigerant can flow, in which the expansion valve is arranged as the first expansion valve (15), by means of which the first partial mass flow can be adjusted and expanded, and the condenser (14), by means of which the first partial mass flow can be condensed; ◯ a bypass line (16) connected in parallel to the condenser line (12) and in series with the compressor line (9) and through which a second partial mass flow of the refrigerant can flow, in which a second expansion valve (18) is arranged, by means of which the second partial mass flow can be adjusted and expanded; and o a mixing point (M) at which the condenser branch (12) and the bypass branch (16) are brought together and the first partial mass flow and the second partial mass flow can be brought together to form a total mass flow and can thus be mixed with one another. [3] Tempering device (6) according to claim 2, characterized by that the separation device (32) is arranged upstream of the refrigerant compressor (11), downstream of the first expansion valve (15), downstream of the condenser (14) and downstream of the second expansion valve (18). [4] Tempering device (6) according to claim 2 or 3, characterized by that the separating device (32) is arranged at the mixing point (M). [5] Tempering device (6) according to claim 2 or 3, characterized by that the separation device (32) is arranged in the compressor train (9) upstream of the refrigerant compressor (11) and downstream of the mixing point (M). [6] Tempering device (6) according to claim 2 or 3, characterized by that the separation device (32) is arranged in the condenser branch (12) downstream of the condenser (14), downstream of the first expansion valve (15) and upstream of the mixing point (M). [7] Tempering device (6) according to claim 2 or 3, characterized by that the separation device (32) is arranged in the bypass line (16) downstream of the second expansion valve (18) and upstream of the mixing point (M). [8] Tempering device (6) according to one of the preceding claims, characterized by that the heating element (33) is designed as an electrical heating element. [9] Tempering device (6) according to one of the preceding claims, characterized by that the separation device (32) has a collecting area (44) for collecting the separated liquid phase (37). [10] Method for operating a temperature control device (6) according to one of the preceding claims. [11] Motor vehicle, with at least one temperature control device (6) according to one of claims 1 to 9.

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