DE102023111037A1 - Tempering device for tempering at least a partial area of a motor vehicle, method for operating a tempering device and motor vehicle - Google Patents

Abstract

The invention relates to a temperature control device (6) for controlling the temperature of at least a partial region of a motor vehicle, with a refrigerant circuit (7) through which a refrigerant flows, which has a compressor train (9) through which the refrigerant can flow and in which a refrigerant compressor (11) is arranged, by means of which the refrigerant is to be conveyed and compressed, and a condenser train (12) connected in series with the compressor train (9) and thus through which a first partial mass flow of the refrigerant can flow, in which a first expansion valve (15) by means of which the first partial mass flow can be adjusted and expanded, and a condenser (14) by means of which the first partial mass flow can be condensed are arranged. The refrigerant circuit (7) comprises a bypass line (16) which is connected parallel to the condenser line (12) and serially to the compressor line (9) and can thus be flowed through by a second partial mass flow of the refrigerant, in which a second expansion valve (18) is arranged, by means of which the second partial mass flow can be adjusted and expanded.

Description

The invention relates to a temperature control device for controlling the temperature of at least one part of a motor vehicle. The invention also relates to a method for operating such a temperature control device. The invention also relates to a motor vehicle with at least one such temperature control device.

The JP 5861 495 B2 discloses a temperature control device for a vehicle. Furthermore, the EP 2 265 453 B1 a cooling arrangement for cooling a temperature-sensitive unit of a motor vehicle is known. In addition, the DE 603 20 060 T2 a method for operating a cooling system.

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

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 23 and by a motor vehicle having the features of patent claim 14. Advantageous embodiments of the invention are the subject of the dependent claims.

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 area 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, has the temperature control device in its fully manufactured state, by means of which at least the said partial area 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 area of the motor vehicle is temperature controlled, i.e. cooled and/or heated, by means of the temperature control device. For example, the partial 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 people such as the driver of the motor vehicle can stay while the motor vehicle is traveling. Alternatively or additionally, the partial 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. Thus, the motor vehicle is, 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 electrical machine by means of which the motor vehicle can be driven, in particular purely electrically. Preferably, the electrical machine is a high-voltage component whose electrical voltage, in particular electrical operating or nominal voltage, is preferably greater than 50 volts, in particular preferably greater than 60 volts, and very preferably amounts to several hundred volts. For example, the electrical machine can be supplied with the electrical energy stored in the electrical energy storage device, whereby the electrical machine can be operated in a motor mode and thus as an electric motor by means of which the motor vehicle can be driven, in particular purely electrically.

The temperature control device has a refrigerant circuit, also simply referred to as a circuit or refrigerant circuit, through which a refrigerant can flow and is flowed through in particular during the method. 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 refrigerant can or does flow through the compressor train. The refrigerant circuit also has a refrigerant compressor, also referred to as a compressor or condenser, 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, in the method it is provided that the refrigerant is conveyed and compressed by means of the refrigerant compressor.

The refrigerant circuit also has a condenser branch which is connected in series with the compressor branch in terms of flow technology and through which a first partial mass flow of the refrigerant can flow, 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. In the condenser branch, a first expansion valve is arranged, by means of which the first partial mass flow can be adjusted and expanded. Thus, for example, the method provides for the first partial mass flow to be expanded by means of the first expansion valve. Thus, several 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. In addition, a capacitor is arranged in the capacitor branch, by means of which the first partial mass flow can be condensed, in particular in a targeted manner. 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 capacitor. By condensing the first partial mass flow, the first partial mass flow is or will be cooled.

The refrigerant circuit also has a bypass branch which is fluidically connected in series with the compressor branch and fluidically parallel to the condenser branch and can therefore 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 apart from one another, in particular in the flow direction of the refrigerant flowing through the refrigerant circuit. In particular, for example, the method provides for the second partial mass flow to flow through the bypass branch. A second expansion valve is arranged in the bypass line, by means of which the second partial mass flow can be adjusted and expanded. Thus, in particular, the method provides for the second partial mass flow to be 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 to mean that several 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. that different values of the respective flow cross-section can be adjusted.

The first partial mass flow can or will flow through or through the first expansion valve, and the second expansion valve can or will flow through or through the second partial mass flow. The refrigerant compressor and thus, for example, the compressor train, that is to say at least part of the compressor train, can or will be 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 thus formed at least by the first partial mass flow and by the second partial mass flow. In addition, the second partial mass flow can or will flow through or through the condenser. The condenser is, for example, a heat exchanger which, for example, can be operated or functions as the aforementioned condenser at least in one mode, in particular at least in a heat pump mode, of the temperature control device. For example, a fluid provided in addition to the refrigerant can flow through and/or around the condenser. For example, heat can be transferred from the coolant to the fluid via the condenser, whereby the coolant is cooled and the fluid is heated, particularly in the operation mentioned. Heat contained in the coolant can thus be used to heat the fluid. The fluid can, for example, be supplied to the partial area in order to heat the partial area and thereby temper it by means of the fluid, in particular by means of the heat that has passed from the coolant to the fluid via the condenser. In more general terms, the partial area can, for example, be tempered, in particular heated, by means of the fluid, in particular by means of the heat contained in the fluid that has passed 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 partial area, in particular into the interior space mentioned, in order to temper, in particular heat, the interior space by means of the fluid. It is also conceivable that the fluid is a liquid. For example, the electrical energy storage device can be tempered, in particular heated, by means of the fluid. For this purpose, for example, the electrical energy storage device is supplied with the fluid. In particular, the operation mentioned is, for example, a heat pump operation.

The heat that has passed from the coolant to or to the fluid via the condenser can, for example, pass 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 can be or is transferred from the coolant to or to the fluid via the condenser, comes, for example, at least predominantly or exclusively from the coolant compressor or is at least predominantly or exclusively caused by the coolant compressor or fed into the coolant, in particular by compressing the coolant by means of the coolant compressor and thereby heating it. The coolant compressor can thus be used as a heat source to heat the coolant and, in particular via the condenser, for example the fluid and subsequently to heat the partial area.

Furthermore, it is provided that the bypass line and the condenser line are brought together at, in particular, 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 can be or are brought together to form a total mass flow, and at the mixing point, the first partial mass flow and the second partial mass flow can be or are mixed with one another, in that the first partial mass flow and the second partial mass flow can be or are brought together to form the total mass flow at the mixing point. The compressor flow flowing through the refrigerant compressor thus 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 comprises exclusively 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 coolant, so that in the second operating state the compressor flow is formed, in particular exclusively, by the first partial mass flow, the second partial mass flow and the at least or exactly one further partial mass flow of the coolant. 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 be introduced into the compressor train, for example, and thus flow in and subsequently flow through the compressor train and in particular the coolant compressor. Since the first partial mass flow and the second partial mass flow result in or form the total mass flow by the first partial mass flow and the second partial mass flow being brought together and thereby mixed with one another, the first partial mass flow and the second partial mass flow, each considered individually, are less than the total mass flow and the compressor flow. In addition, the further partial mass flow, considered individually, is less than the compressor flow and, for example, than the total mass flow.

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 coolant 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 branches off at the overall branching point into the first partial mass flow and the second partial mass flow, and is thus divided.

In the method for operating the temperature control device, a first pressure and a first temperature of the coolant, in particular of the compressor flow flowing through the coolant compressor, are determined in the compressor train upstream of the coolant compressor and downstream of the mixing point, for example by means of an electronic computing device, in particular the temperature control device, in particular of the motor vehicle. The first pressure of the coolant, in particular of the compressor flow, is to be understood as a pressure of the coolant, in particular of the compressor flow, wherein the first pressure prevails at a first pressure point that is arranged in the compressor train upstream of the coolant compressor and downstream of the mixing point. The first temperature of the coolant, in particular of the compressor flow, is to be understood as a temperature of the coolant, in particular of the compressor flow, wherein the first temperature prevails at a first temperature point that is arranged in the compressor train upstream of the coolant compressor and downstream of the mixing point. For example, the first pressure point and the first temperature point coincide.

By means of the electronic computing device, a second pressure and a second temperature of the refrigerant downstream of the refrigerant compressor, upstream of the condenser and upstream of the expansion valves. The second pressure of the refrigerant is to be understood as a pressure of the refrigerant, the second pressure prevailing at a second pressure point which is arranged downstream of the refrigerant compressor and upstream of the condenser and upstream of the expansion valves, the second pressure point being 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 expansion valves are mentioned above and below, this means the first expansion valve and the second expansion valve, unless otherwise stated. The second temperature of the refrigerant is understood to mean a temperature of the refrigerant, the second temperature prevailing at a second temperature point that is arranged downstream of the refrigerant compressor, upstream of the condenser and upstream of the expansion valves, the second temperature point being arranged 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 line and very particularly upstream of the branch points.

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 which is 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 which is 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 can coincide.

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, at least through part of the compressor train. The pressures and temperatures are determined using the electronic computing device, which is explained in more detail below.

In the method, the expansion valves are controlled by means of the electronic computing device 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 set as a function of the determined temperatures and as a function of the determined pressures. When reference is made to the partial mass flows previously and subsequently, this means the first partial mass flow and the second partial mass flow, unless otherwise stated. This means that the partial mass flows are set, in particular varied, as a function of the determined pressures and as a function of the determined temperatures by means of the electronic computing device via the expansion valves, in other words by controlling the expansion valves, for example by adjusting, in other words by varying, the said flow cross sections of the expansion valves by controlling the expansion valves. As a result, 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, can be set in a particularly advantageous manner, so that robust operation of the temperature control device and, as a result, effective and efficient temperature control can be achieved. In particular, by setting the first partial mass flow and the second partial mass flow and thus by setting the mixing ratio, it is possible to avoid the refrigerant compressor being supplied with wet steam or even liquid. In other words, for example, it is possible to avoid 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, comprising wet steam or even liquid, so that undesirable damage to the temperature control device can be avoided. Furthermore, it is possible to achieve particularly advantageous temperature control of the partial area without the need for any cooling in the refrigerant circuit or in an additional chen, for tempering the partial area and through which the fluid can flow, for example, an electric continuous-flow heater is arranged. Furthermore, a heat exchanger arranged in the refrigerant circuit and, for example, in the tempering circuit, also referred to as a chiller and operable or operated as an evaporator, for example, can be dispensed with, so that the number of parts and thus the weight and costs of the tempering device can be kept particularly low. At the same time, it is possible to set the partial mass flows and thus the mixing ratio in such an advantageous way that the total mass flow has a particularly advantageous state, in particular state of aggregation, in particular such that, for example, the enthalpy of the total mass flow lies to the right of the dew line of the refrigerant, for example in the form of R1234yf, in particular in a phase diagram of the refrigerant, wherein, for example, the, in particular 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.

In order to be able to implement particularly efficient operation of the temperature control device, in particular of the refrigerant compressor, the temperature control device has a heat accumulator designed to store heat. In other words, heat is to be stored by means of the heat accumulator, i.e. in the heat accumulator. This means in particular that heat can optionally be stored in the heat accumulator and thus stored in the heat accumulator, or the heat accumulator can release heat stored in the heat accumulator. The heat accumulator has an inlet area via which the refrigerant can be fed to the heat accumulator, so that heat from the refrigerant fed to the heat accumulator via the inlet area can optionally be stored in the heat accumulator or heat stored in the heat accumulator can be transferred from the heat accumulator to the refrigerant fed to the heat accumulator via the inlet area. In particular, the heat accumulator can be flowed through by the coolant supplied to the heat accumulator via the inlet area, so that heat from the coolant supplied to the heat accumulator via the inlet area and flowing through the heat accumulator can either be stored in the heat accumulator or heat stored in the heat accumulator can be transferred from the heat accumulator to the coolant supplied to the heat accumulator via the inlet area and flowing through the heat accumulator.

Furthermore, the heat accumulator has an outlet region via which the coolant fed to the heat accumulator via the inlet region and flowing through the heat accumulator can be discharged from the heat accumulator, i.e. in particular can be discharged from the heat accumulator, after the coolant has been fed to the heat accumulator via the inlet region. This means, for example, that the coolant can flow through the heat accumulator in such a way that the coolant can flow from the inlet region to the outlet region and thereby flow through the heat accumulator. In other words, the coolant flows from the inlet region to the outlet region on its way through the heat accumulator. The outlet region is thus arranged downstream of the inlet region. Thus, for example, the method provides that, in particular in the aforementioned operation, the coolant is supplied to the heat accumulator via the inlet area, so that the coolant flows into the heat accumulator via the inlet area, flows through the heat accumulator and flows from the inlet area to the outlet area and flows out of the heat accumulator via the outlet area, and is thus discharged from the heat accumulator. Heat can or will be exchanged between the coolant flowing through the heat accumulator and flowing from the inlet area to the outlet area and the heat accumulator, that is to say, for example, between the coolant flowing through the heat accumulator and flowing from the inlet area to the outlet area and at least one storage element of the heat accumulator, in particular while the coolant flows through the heat accumulator, so that heat is optionally transferred from the coolant flowing through the heat accumulator to the heat accumulator or heat is transferred from the heat accumulator to the coolant flowing through the heat accumulator. If heat is transferred from the coolant flowing through the heat storage unit to the heat storage unit, the heat that is transferred from the coolant to the heat storage unit is stored in the heat storage unit and thus stored in the heat storage unit. This cools the coolant. If heat is transferred from the heat storage unit to or onto the coolant flowing through the heat storage unit, the coolant is heated and heat is stored out of the heat storage unit.

It is very preferably provided that the first expansion valve is arranged in the condenser branch downstream of the condenser and in particular upstream of the mixing point. Furthermore, the temperature control device has a valve device which can be switched between a first switching state and a second switching state. In particular, the valve device The valve device can be switched between the first switching state and the second switching state by controlling the valve device. For example, the valve device can be controlled by supplying the valve device with electrical energy. In other words, the valve device can be controlled by supplying the valve device with electrical energy. In the first switching state, the heat accumulator is connected to the refrigerant circuit by means of the valve device in such a way that in the first switching state the heat accumulator is fluidically connected to the refrigerant circuit at a first connection point arranged downstream of the refrigerant compressor, upstream of the condenser branch and upstream of the bypass branch in the refrigerant circuit, in particular in the compressor branch, and at a second connection point arranged upstream of the refrigerant compressor in the refrigerant circuit, in particular in the compressor branch, which is arranged in the refrigerant circuit, in particular in the compressor branch, downstream of the first expansion valve and/or downstream of the second expansion valve, whereby in the first switching state at least a portion of the refrigerant compressed by means of the refrigerant compressor can be fed to the heat accumulator via the inlet region from the first connection point and the refrigerant discharged from the heat accumulator via the outlet region can be introduced into the refrigerant circuit at the second connection point. Thus, for example, in the first switching state, the heat accumulator is connected to the refrigerant circuit by means of the valve device in such a way that the heat accumulator is connected fluidically parallel to the bypass branch and fluidically parallel to the condenser branch and fluidically serially to the compressor branch, in particular in such a way that at least a portion of the refrigerant compressed by means of the refrigerant compressor can be fed to the heat accumulator via the inlet area. Thus, for example, in the first switching state, a third partial mass flow of the refrigerant can be fed from the first connection point to the heat accumulator via the inlet area, wherein the third partial mass flow is or will be formed by the refrigerant compressed by means of the refrigerant compressor, that is to say by a portion of the refrigerant compressed by means of the refrigerant compressor. The third partial mass flow is thus the said portion of the refrigerant compressed by means of the refrigerant compressor, which can be fed to the heat accumulator via the inlet area in the first switching state. In this case, it is particularly conceivable that the third partial mass flow is discharged from the heat accumulator via the outlet area and introduced into the refrigerant circuit at the second connection point. In particular, the third partial mass flow is the previously mentioned further partial mass flow, so that, for example, in the first switching state, the compressor flow comprises, for example, in particular exclusively, the total mass flow and at least or exactly the third partial mass flow of the refrigerant, so that in the first switching state, the compressor flow is formed, in particular exclusively, by the first partial mass flow, the second partial mass flow and the third partial mass flow of the refrigerant. It can thus be provided, for example, that the valve device is in the first switching state in the previously mentioned second operating state.

In particular, the second connection point can coincide with the mixing point, or the second connection point is arranged downstream of the mixing point, in particular in the compressor line. It is also conceivable that the second connection point is arranged upstream of the mixing point and in the condenser line or in the bypass line. The first connection point can, for example, coincide with the first branch point and/or with the second branch point and/or with the overall branch point, or the first connection point is spaced apart from the first branch point and/or from the second branch point and/or from the overall branch point. In particular, it can be provided that in the first switching state at the first connection point the compressor flow branches into the first partial mass flow, the second partial mass flow and the third partial mass flow, or in the first switching state, for example, the compressor flow branches at the first connection point into the third partial mass flow and the further mass flow, which then branches, for example, at the total branch point into the first partial mass flow and the second partial mass flow.

In the second switching state, the heat accumulator is connected to the refrigerant circuit by means of the valve device in such a way that in the second switching state, the heat accumulator is fluidically connected to the refrigerant circuit at a third connection point arranged upstream of the refrigerant compressor in the refrigerant circuit, in particular in the compressor line, which is arranged in the refrigerant circuit downstream of the first expansion valve and/or downstream of the second expansion valve. The third connection point can coincide with the mixing point, or the third connection point is preferably arranged downstream of the mixing point.

In the second switching state, the heat accumulator is connected to the refrigerant circuit by means of the valve device in such a way that in the second switching state the heat accumulator is connected to a downstream the third connection point and upstream of the refrigerant compressor in the refrigerant circuit, in particular in the compressor train, is fluidically connected to the refrigeration circuit, whereby in the second switching state at least a portion of the total mass flow, in particular the entire mass flow, can be fed to the heat accumulator via the inlet region from the third connection point and the refrigerant discharged from the heat accumulator via the outlet region can be introduced into the refrigeration circuit at the fourth connection point. In particular, it is provided that the third connection point can be flowed through by the, in particular the entire, total mass flow.

Thus, for example, in the second switching state, the heat accumulator is connected to the refrigerant circuit by means of the valve device in such a way that the heat accumulator is connected in fluidic series with the bypass branch, in fluidic series with the condenser branch and in fluidic series with the refrigerant compressor, in particular in such a way that the heat accumulator is arranged downstream of the condenser branch, downstream of the bypass branch and upstream of the refrigerant compressor. Thus, for example, in the second switching state, the compressor flow flowing through the refrigerant compressor comprises, in particular exclusively, the total mass flow, so that in the second switching state the compressor flow is formed, in particular exclusively, by the first partial mass flow and the second partial mass flow of the refrigerant. Thus, for example, it can be provided that the valve device is in the second switching state in the aforementioned first operating state.

Since the refrigerant compressor compresses the refrigerant and thereby heats it, for example in the first switching state the refrigerant compressed by the refrigerant compressor and thereby heated can be supplied to the heat accumulator in particular in the form of the third partial mass flow, so that heat can pass from the refrigerant to the heat accumulator and thus be stored in the heat accumulator. Thus, in the first switching state the heat accumulator is fluidically connected via the inlet area or the inlet area to a high-pressure side of the refrigerant compressor, also referred to as the high-pressure area, with the refrigerant compressor providing the refrigerant compressed by the refrigerant compressor on or via its high-pressure side. In the second switching state the refrigerant expanded by means of the first expansion valve and/or by means of the second expansion valve can be supplied to the heat accumulator via the inlet area, in particular in the form of the total mass flow, since in the second switching state the heat accumulator is fluidically connected to the refrigerant circuit via the inlet area or the inlet area at the third connection point. Thus, in the second switching state, the heat accumulator is fluidically connected via the inlet region or the inlet region to a low-pressure side of the refrigerant compressor, also referred to as the low-pressure region. Thus, for example, in the second switching state, heat can be transferred from the heat accumulator to or onto the refrigerant flowing through the heat accumulator, in particular to or onto the total mass flow or compressor flow, whereby the refrigerant is heated, namely before the refrigerant flows through the refrigerant compressor. Since the fourth connection point is arranged downstream of the third connection point and upstream of the refrigerant compressor, the refrigerant compressor is supplied with the refrigerant that is or was heated by means of the heat accumulator and thus by heat being transferred from or from the heat accumulator to the refrigerant. The invention thus enables particularly efficient operation of the temperature control device. In particular, the invention makes it possible, by using the heat accumulator, to operate the refrigerant compressor with such a power, in particular electrical, of the refrigerant compressor that the refrigerant compressor can be operated at an efficient operating point, in particular independently of a power requirement of the condenser, that is to say, for example, independently of a power with which the condenser is operated or supplied.

If, for example, in the second operating state of the temperature control device, the condenser is operated or supplied with such a power that the refrigerant compressor would have to be operated with a power of, for example, two kilowatts without using the heat accumulator, then by using the heat accumulator and in the first switching state of the valve device, the refrigerant compressor can now be operated with a power of more than two kilowatts and thus much more efficiently, and thus more efficiently, because excess power of the refrigerant compressor, whose excess power is not required to operate the condenser, can now be stored as heat in the heat accumulator. It is therefore possible, for example, to operate the refrigerant compressor in the second operating state not with two kilowatts, but with a power of, for example, six kilowatts. Two of these six kilowatts of power of the refrigerant compressor can be used to operate the condenser, and the remaining four kilowatts of power of the refrigerant compressor can used to store heat in the heat storage unit. The heat stored in the heat storage unit can then be used later, for example in the first operating state, in order to enable particularly efficient operation of the refrigerant compressor in the first operating state.

If, for example, the condenser is operated or supplied with such a power in the first operating state of the temperature control device that the refrigerant compressor would have to be operated with a power of, for example, nine kilowatts without using the heat accumulator, then by using the heat accumulator and in the second switching state of the valve device, the refrigerant compressor can now be operated with a power of less than nine kilowatts and thus much more efficiently, and therefore with greater efficiency, because the heat stored in the heat accumulator can be used to heat the refrigerant. The refrigerant can therefore be heated in the second switching state and thus, for example, in the first operating state both by means of the refrigerant compressor and by means of heat from the heat accumulator. In other words, the heat accumulator, i.e. the heat stored in the heat accumulator, which was stored in the heat accumulator in the second operating state, for example, can support the refrigerant compressor in heating the refrigerant in the first operating state. It is therefore possible, for example, to operate the refrigerant compressor in the first operating state not with nine kilowatts, but with an output of, for example, six kilowatts. The three kilowatts of output missing to operate the condenser is compensated for or provided, for example, by transferring heat from the heat accumulator to the refrigerant. As a result, the refrigerant has such a high heat level before it is compressed by the refrigerant compressor that an output of six kilowatts from the refrigerant compressor is sufficient to compress and heat the refrigerant by means of the refrigerant compressor, starting from the heat level, in such a way that the compressed refrigerant downstream of the refrigerant compressor, upstream of the bypass line and upstream of the condenser line has a temperature that the refrigerant would have if the heat accumulator were not used and, in particular, alone, i.e. without the heat accumulator, the refrigerant compressor would compress the refrigerant with an output of nine kilowatts. It can be seen that in both operating states the refrigerant compressor could be operated with, for example, six kilowatts and thus particularly efficiently, so that a particularly efficient and low-efficiency operation of the temperature control device can be achieved.

It can also be seen that the refrigerant compressor in the first switching state and in the second switching state can convey the refrigerant, in particular via the inlet area, to the heat accumulator and, in particular via the outlet area, away from the heat accumulator and can thereby convey it in particular through the heat accumulator.

In order to be able to implement particularly efficient operation of the temperature control device, one embodiment of the invention provides that the heat storage device is designed as a latent heat storage device, which is also referred to as a phase change storage device or PCM storage device (PCM - Phase Change Material). The latent heat storage device has at least one phase change material for storing the heat. The phase change material is thus, for example, the aforementioned storage element.

In order to also realize a particularly robust operation of the temperature control device and thus to be able to protect the refrigerant compressor in particular from undesirable operating conditions, which can result in a particularly long service life of the refrigerant compressor, it is also provided according to the invention that the temperature control device has at least or exactly one additional pump provided in addition to the refrigerant compressor, which is designed, for example, as an electric pump, thus as an electrically operated pump. The refrigerant can be pumped through the heat accumulator by means of the additional pump while the refrigerant compressor is deactivated, i.e. while operation of the refrigerant compressor and thus pumping of the refrigerant by means of the refrigerant compressor are not taking place. Furthermore, it is preferably provided that the refrigerant can be pumped through the condenser branch and/or through the bypass branch by means of the additional pump while the refrigerant compressor is deactivated, i.e. while pumping of the refrigerant by means of the refrigerant compressor is not taking place. The bypass line and the condenser line are collectively also referred to as delivery lines, so that the refrigerant can be pumped through the heat accumulator and through at least or exactly one of the delivery lines, preferably by means of the additional pump, while the refrigerant compressor is deactivated.

The feature that the additional pump pumps the coolant through the heat storage can be conveyed through while the refrigerant compressor is deactivated, it is to be understood that the additional pump can convey the refrigerant to the heat accumulator and away from the heat accumulator and in doing so can convey it through the heat accumulator while the refrigerant compressor is deactivated. The invention thus makes it possible to convey the refrigerant through the heat accumulator by means of the additional pump and to heat it by means of the heat accumulator, that is to say by means of heat stored in the heat accumulator, without operating the refrigerant compressor. This can be implemented in such a way that heat stored in the heat accumulator can be transferred from or out of the heat accumulator to or onto the refrigerant while the refrigerant is conveyed through the heat accumulator and, for example, also through at least or exactly one conveying line by means of the additional pump and while the refrigerant compressor is deactivated, and therefore not operated.

In particular, the invention enables a particularly advantageous start-up or shutdown of the temperature control device, in particular from a wet or wet vapor phase of the coolant, to be achieved without a liquid phase or a phase of the coolant designed as a wet vapor phase flowing through the coolant compressor or being conveyed by the coolant compressor. In other words, for example, the coolant can be conveyed particularly advantageously through the heat accumulator and through the at least one or exactly one conveying line by means of the additional pump even if the coolant is at least partially designed as wet vapor or as a liquid. This means that the coolant can be avoided from being conveyed by means of the coolant compressor when the coolant is at least partially designed as wet vapor or liquid, so that undesirable damage to the coolant compressor can be avoided.

Preferably, it is provided that compression of the coolant caused by the additional pump is avoided, in particular always. In other words, it is provided that compression of the coolant caused by the additional pump is avoided when and preferably always when the additional pump conveys the coolant, so that preferably the additional pump does not compress the coolant when and preferably always when it conveys the coolant through the heat accumulator and preferably also through the at least or exactly one conveying line. Thus, preferably the conveying pump is not a compressor for compressing the coolant, so that undesirable damage to the additional pump can also be avoided.

Furthermore, it is preferably provided that when the additional pump conveys the coolant through the heat accumulator and through the at least or exactly one conveying line, the expansion valve arranged in the at least or exactly one conveying line, in particular the second expansion valve, is fully open, so that, for example, when the additional pump conveys the coolant through the heat accumulator and through the at least or exactly one conveying line and thus through the expansion valve arranged in the at least one conveying line, the coolant flows through the expansion valve arranged in the at least or exactly one conveying line at least substantially without pressure loss and/or at least substantially without phase transformation. This makes it possible to avoid excessive pressure losses of the coolant and to avoid undesirable phase transformations of the coolant.

In order to be able to implement a particularly advantageous, efficient and robust operation of the temperature control device, it is provided in one embodiment of the invention that the valve device can be switched to a third switching state, in which the heat accumulator and the additional pump, which in the third switching state is fluidically connected in series with the heat accumulator, are fluidically connected to the refrigerant circuit at a tapping point arranged upstream of the refrigerant compressor in the refrigerant circuit, in particular in the compressor line, which is arranged in the refrigerant circuit downstream of the first expansion valve and/or downstream of the second expansion valve, and at an inlet point arranged downstream of the refrigerant compressor, upstream of the condenser line and upstream of the bypass line in the refrigerant circuit, in particular in the compressor line, whereby the refrigerant can be conveyed from the tapping point to the inlet point by means of the additional pump, bypassing the refrigerant compressor, i.e. without the refrigerant flowing through the refrigerant compressor, and thereby through the heat accumulator and, for example, through which at least or exactly one conveying line can be conveyed while bypassing the refrigerant compressor, i.e. without the refrigerant flowing through the refrigerant compressor, while the refrigerant compressor is deactivated.

The feature that the refrigerant can be conveyed from the tap point to the inlet point bypassing the refrigerant compressor and can thereby be conveyed through the heat accumulator means that the refrigerant conveyed by means of the additional pump on its way from the The tap point to the inlet point bypasses the refrigerant compressor and therefore does not flow through the refrigerant compressor. This can safely prevent undesirable damage or stress on the refrigerant compressor.

Preferably, it is provided that in the third switching state the additional pump is arranged in fluidically serial relation to the heat accumulator such that, for example, the additional pump is arranged downstream of the tapping point and upstream of the inlet point, in particular downstream of the tapping point and upstream of the heat accumulator.

Another embodiment is characterized by the fact that the tapping point coincides with the third connection point. This ensures particularly efficient and robust operation.

In a further, particularly advantageous embodiment of the invention, it is provided that the inlet point coincides with the first connection point, whereby a particularly efficient and robust operation can be ensured.

In order to be able to implement a particularly advantageous, in particular particularly efficient, operation of the temperature control device, it is provided in a further embodiment of the invention that in the first switching state and in the second switching state the coolant can be conveyed through the inlet area to the heat accumulator by means of the coolant compressor, bypassing the additional pump, i.e. without the coolant flowing through the additional pump, and can be conveyed away from the heat accumulator via the outlet area. This means that the coolant conveyed in the first switching state and in the second switching state by means of the coolant compressor bypasses the additional pump on its way from the inlet area to the outlet area of the heat accumulator and thus through the heat accumulator, and therefore does not flow through the additional pump. This makes it possible to avoid an excessive pressure loss of the coolant, which means that a particularly efficient, and therefore high-efficiency, operation of the temperature control device can be achieved.

In order to achieve particularly efficient operation, it has proven particularly advantageous if the phase change material has a melting temperature which lies in a range from 50 degrees Celsius to 90 degrees Celsius inclusive.

In order to be able to realize a particularly efficient operation, it is provided in a further embodiment of the invention that the melting temperature of the phase change material is in a range from 75 degrees Celsius to 90 degrees Celsius inclusive.

In a further, particularly advantageous embodiment of the invention, it is provided that the melting temperature is in a range from 75 degrees Celsius to 80 degrees Celsius. This can ensure particularly efficient operation.

A further embodiment is characterized in that the melting temperature of the phase change material is in a range from 50 degrees Celsius to 80 degrees Celsius. This allows a particularly efficient and therefore efficient operation of the temperature control device.

In order to be able to operate the temperature control device particularly efficiently and thus with a favorable efficiency, a further embodiment of the invention provides that the temperature control device has a third expansion valve, which is provided in particular in addition to the first expansion valve and in addition to the second expansion valve, which in the first switching state, preferably based on the switching states exclusively in the first switching state, is connected in series with the heat accumulator in such a way that in the first switching state the third expansion valve is arranged downstream of the first connection point and upstream of the second connection point. The third expansion valve can be used to adjust and expand the aforementioned third partial mass flow of the coolant flowing through the heat accumulator in the first switching state. The previous and following statements on the first expansion valve and the second expansion valve can also be easily transferred to the third expansion valve and vice versa.

In order to be able to realize a particularly efficient and thus efficient operation of the temperature control device, it is provided in a further embodiment of the invention that in the first switching state the third expansion valve is connected in series with the heat accumulator in such a way that in the first switching state the third expansion valve is arranged downstream of the heat accumulator and upstream of the second connection point.

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 described as advantages and advantageous embodiments designs of the second aspect of the invention and vice versa.

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.

For example, the third expansion valve is arranged in fluidic series with the heat accumulator even when the coolant is pumped through the heat accumulator by means of the additional pump. In particular, it is conceivable that in the third switching state of the valve device the third expansion valve is arranged in fluidic series with the heat accumulator, in particular such that in the third switching state the third expansion valve is arranged downstream of the tapping point and upstream of the inlet point and in particular downstream of the tapping point and upstream of the heat accumulator, in particular with respect to a first flow direction in which in the third switching state the coolant flows from the tapping point to the inlet point and in the process flows through the heat accumulator and also the third expansion valve. The first flow direction is, for example, opposite to a second flow direction in which the coolant flows in the first switching state of the valve device from the first connection point to the second connection point and in the process flows through the heat accumulator and also through the third expansion valve.

• 1 eine schematische Darstellung einer Temperiereinrichtung zum Temperieren zumindest eines Teilbereichs eines Kraftfahrzeugs;
• 2 eine schematische Darstellung der Temperiereinrichtung, wobei sich eine Ventileinrichtung der Temperiereinrichtung in einem ersten Schaltzustand befindet;
• 3 eine schematische Darstellung der Temperiereinrichtung, wobei sich die Ventileinrichtung in einem zweiten Schaltzustand befindet;
• 4 eine schematische Darstellung der Temperiereinrichtung, wobei sich die Ventileinrichtung in einem dritten Schaltzustand befindet;
• 5 eine schematische Darstellung der Temperiereinrichtung, wobei sich die Ventileinrichtung in einem vierten Schaltzustand befindet; und
• 6 ein Phasendiagramm eines Kältemittels, welches einen Kältemittelkreislauf der Temperiereinrichtung bei einem Verfahren zum Betreiben der Temperiereinrichtung durchströmt.

Further details of the invention emerge from the following description of a preferred embodiment with the associated drawings.

• 1 a schematic representation of a tempering device for tempering at least a partial area of a motor vehicle;
• 2 a schematic representation of the tempering device, wherein a valve device of the tempering device is in a first switching state;
• 3 a schematic representation of the temperature control device, wherein the valve device is in a second switching state;
• 4 a schematic representation of the temperature control device, wherein the valve device is in a third switching state;
• 5 a schematic representation of the temperature control device, wherein the valve device is in a fourth switching state; and
• 6 a phase diagram of a refrigerant which flows through a refrigerant circuit of the temperature control device in a method for operating the temperature control device.

In the figures, identical or functionally identical elements are provided with identical reference symbols.

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. At least a partial area of the motor vehicle can be temperature-controlled, i.e. heated or cooled, by means of the temperature control device 6. 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, 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 coolant circuit 7 through which a coolant can flow, which is flowed through by the coolant during the method and thus during operation of the temperature control device 6, which is operated during operation according to the method.

The refrigerant circuit 7 has a compressor line 9 through which the refrigerant can flow. A refrigerant compressor 11 is arranged in the compressor line 9, by means of which the refrigerant can be conveyed and compressed. In the operation mentioned 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 part of the compressor line 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 designed as a mass flow of the refrigerant, which is explained in more detail below.

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 which branches off from the compressor branch 9 at a branch point A and can thus be flowed through by a first partial mass flow of the refrigerant. In the condenser branch 12, a A condenser 14, also referred to as a condenser, is arranged by means of which the first partial mass flow, i.e. the coolant flowing through the condenser branch 12, can be or is condensed, i.e. liquefied. In addition, 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. In addition, the first partial mass flow, i.e. the coolant flowing through the condenser branch 12, can be or is expanded by means of the expansion valve 15.

The refrigerant circuit 7 also has a bypass line 16 which is connected in terms of flow parallel to the condenser line 12 and in terms of flow series to the compressor line 9 and in this case branches off from the compressor line 9 at the branch point A and can thus be flowed through by a second partial mass flow of the refrigerant. Since both the bypass line 16 and the condenser line 12 branch off from the compressor line 9 at the branch point A, the branch point A is a complete branch point.

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

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 thus be mixed with one another, and thus brought together in the process and thus 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 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 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.

By means of a 1 A first pressure and a first temperature of the refrigerant, in particular of the compressor flow, in the compressor line 9 upstream of the refrigerant compressor 11 and downstream of the mixing point M are determined by the electronic computing device 19 shown particularly schematically. 1 In the embodiment shown, 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. In 1 1 designates a first point, which is also referred to as the first location. The first point 1 is arranged in the compressor line 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 line 9 at the point 1.

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 1 In the embodiment shown, a second sensor device S2 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 which 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 1 a second point is designated with 2, wherein the second point is also referred to as the second point. 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 line 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 line 12 and the bypass line 16 branch off from the compressor line 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.

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 1 shown embodiment in the capacitor train 12 downstream of the capacitor 14 and upstream of the mixing point M. In the 1 In the embodiment shown, 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 which 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.

The electronic computing device 19 controls the expansion valves 15 and 18 depending on the determined temperatures and depending on the determined pressures, whereby the first partial mass flow and the second partial mass flow are set depending on the determined temperatures and depending on 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, for example, designated by m1, and the second partial mass flow is, for example, designated by m2. The mixing ratio is, for example, designated by Φ. Thus, for example: $$\mathrm{\Phi }=\frac{m1}{\mathrm{<figure-callout\; id="2"\; label="m"\; filenames="DE102023111037A1\_0002.png,DE102023111037A1\_0006.png"\; state="\{\{state\}\}">m</figure-callout>}2}.$$

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 set, 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 set. For example, the expansion valve 18 has a second flow cross-section through which the second partial mass flow can flow, which can be set, 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 set. The electronic computing device 19 controls the actuators, for example, depending on the determined pressures and depending on the determined temperatures, in order to thereby set the flow cross-sections and consequently the partial mass flows and thus the mixing ratio Φ.

In 1 3 denotes a third point, whereby 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 measures sensor device S3 the third pressure and the third temperature at or in the third point 3. Furthermore, in 1 a fourth point is designated with 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 arranged in the condenser line 12 and downstream of the expansion valve 15 and upstream of the mixing point M. Furthermore, in 1 a fifth point is designated with 5, wherein the fifth point 5 is also referred to as the fifth location or is designed as a fifth location. It can be seen that the fifth point 5 is arranged in the bypass line 16 downstream of the expansion valve 18 and upstream of the mixing point M.

In order to be able to implement particularly efficient operation of the temperature control device 6, the temperature control device 6 has a heat accumulator 17 designed to store heat, which in the present case is designed as a latent heat accumulator and thus has at least or exactly one phase change material for storing the heat. The heat accumulator 17 has an input area EB with at least or exactly two inputs, namely a first input E1 and a second input E2. Furthermore, the heat accumulator 17 has an output area AB with at least or exactly two outputs, namely a first output A1 and a second output A2. The coolant can be fed to the heat accumulator 17 via the inlet area EB, so that heat from the coolant fed to the heat accumulator 17 via the inlet area EB and flowing through the heat accumulator 17 can either be stored in the heat accumulator 17 or heat from the heat accumulator 17 can be transferred to the coolant fed to the heat accumulator 17 via the inlet area EB and flowing through the heat accumulator 17. The coolant fed to the heat accumulator 17 via the inlet area EB can be discharged from the heat accumulator 17 via the outlet area AB after it has flowed through the heat accumulator 17 and thereby flowed from the inlet area EB to the outlet area AB.

It can also be seen that the heat accumulator 17 is assigned four branches Z1, Z2, Z and Z4 through which the coolant can flow. The branches Z1 and Z3 are connected to the inlet area EB, and are therefore fluidically connected to the inlet area EB, in this case such that branch Z1 is connected to the inlet E1 and branch Z3 is connected to the inlet E2. The branches Z2 and Z4 are connected to the outlet area AB, and are therefore fluidically connected to the outlet area AB, in this case such that branch Z2 is connected to the outlet A1 and branch Z4 is connected to the outlet A2. The coolant flowing through branch Z1 can therefore be fed to the inlet E1 via branch Z1 and fed to the heat accumulator 17 via the inlet E1 and introduced into the heat accumulator 17. The coolant flowing through branch Z3 can be fed to the inlet E2 via branch Z3 and fed to the heat accumulator 17 via the inlet E2 and introduced into the heat accumulator 17. Via the outlet A1, the refrigerant, after it has flowed through the heat accumulator 17 and flowed from the inlet E1 to the outlet A1, can be discharged from the heat accumulator 17 and introduced into the branch Z2, so that the refrigerant introduced into the branch Z2 can be discharged from the heat accumulator 17 via the branch Z2. Via the outlet A2, the refrigerant, after it has flowed through the heat accumulator 17 and flowed from the inlet E2 to the outlet A2, can be discharged from the heat accumulator 17 and introduced into the branch Z4, so that the refrigerant introduced into the branch Z4 can be discharged from the heat accumulator 17 via the branch Z4.

The temperature control device 6 also comprises a valve device 27, which in the present case has at least or exactly two valves, namely a first valve 28 and a second valve 29. In the embodiment shown in the figures, the respective valve 28, 29 is designed as a 3/2-way valve.

The valve device 27 is arranged between a 2 shown, first switching state and one in 3 shown, second switching state. In the first switching state, the heat accumulator 17 is connected to the refrigerant circuit 7 by means of the valve device 27 in such a way that in the first switching state, the heat accumulator 17 is fluidically connected to the refrigerant circuit 7 at a first connection point V1 arranged downstream of the refrigerant compressor 11, upstream of the condenser branch 12 and upstream of the bypass branch 16 in the refrigerant circuit 7, in particular in the compressor branch 9, and at a second connection point V2 arranged upstream of the refrigerant compressor 11 in the refrigerant circuit 7, in particular in the compressor branch 9, whereby at least a portion of the refrigerant compressed by the refrigerant compressor 11, in particular the compressor flow, can be fed to the heat accumulator 17 via the inlet region EB from the first connection point V1 and the refrigerant discharged from the heat accumulator 17 via the outlet region AB is fed into the refrigerant circuit at the second connection point V2. 7 can be introduced. The second connection point V2 is arranged downstream of the first expansion valve 15 and in this case also downstream of the second expansion valve 18, whereby it would in principle be conceivable that the connection point V2 together with the mixing point M In the case of 1 In the embodiment shown, however, the connection point V2 is arranged downstream of the mixing point M. In the first switching state, at least part of the refrigerant compressed by the refrigerant compressor 11, in particular the compressor flow, can be fed from the first connection point V1 to the heat accumulator 17 via the inlet area EB, in particular via the inlet E1, and in the first switching state, the refrigerant discharged from the heat accumulator 17 via the outlet area AB, in particular via the outlet A1, can be introduced into the refrigerant circuit 7 at the second connection point V2. It can be seen that at least in the first switching state, the inlet E1 is fluidically connected to the refrigerant circuit 7 at the connection point V1 and the outlet A1 is fluidically connected to the refrigerant circuit 7 at the connection point V2, while the inlet E2 and the outlet A2 are fluidically separated from the refrigerant circuit 7, in particular by means of the valve device 27.

In the second switching state, the heat accumulator 17 is connected to the refrigerant circuit 7 by means of the valve device 27 in such a way that in the second switching state, the heat accumulator 17 is fluidically connected to the refrigerant circuit 7 at a third connection point V3 arranged upstream of the refrigerant compressor 11, which is arranged in the refrigerant circuit 7 downstream of the first expansion valve 15 and downstream of the second expansion valve 18, and at a fourth connection point V4 arranged downstream of the third connection point V3 and upstream of the refrigerant compressor 11 in the refrigerant circuit 7, in particular in the compressor line 9, whereby at least a part of the total mass flow, in particular the entire total mass flow, can be fed to the heat accumulator 17 in the second switching state via the inlet area EB, in particular via the inlet E2, from the third connection point V3 and the heat accumulator 17 via the outlet area AB, in particular the outlet A2. discharged refrigerant can be introduced into the refrigerant circuit 7, in particular into the compressor train 9, at the fourth connection point V4.

In principle, it would be conceivable for the third connection point V3 to coincide with the second connection point V2 and/or with the mixing point M. In the present case, however, it is provided that the third connection point V3 is arranged downstream of the mixing point M and in particular upstream of the second connection point V2. Furthermore, it would be conceivable for the connection point V3 to be arranged upstream of the mixing point M and downstream of the expansion valve 18 in the bypass branch 16, or it would be conceivable for the connection point V3 to be arranged downstream of the expansion valve 15 and upstream of the mixing point M in the condenser branch 12.

For example, in the first switching state, a third partial mass flow of the coolant can be supplied to the heat accumulator 17 via the inlet E1 from the connection point V1. At the connection point V2, the third partial mass flow is introduced into the coolant circuit 7 and thereby mixed with the total mass flow, whereby the compressor flow comprises the total mass flow and the third partial mass flow and thus the first partial mass flow and the second partial mass flow and the third partial mass flow, in particular such that the compressor flow is formed exclusively by the first partial mass flow, the second partial mass flow and the third partial mass flow. Thus, for example, the third partial mass flow is the previously mentioned, further partial mass flow.

It can be seen that branch Z1 is connected to the refrigerant circuit 7 at the connection point V1, branch Z2 at the connection point V2, branch Z3 at the connection point V3 and branch Z4 at the connection point V4, both in the first switching state and in the second switching state. In the first switching state, inlet E1 is fluidically connected to the refrigerant circuit 7 via branch Z1 at the connection point V1, and in the first switching state, outlet A1 is fluidically connected to the refrigerant circuit 7 via branch Z2 at the connection point V2. In the first switching state, the branch Z3 and thereby the inlet E2 are fluidically separated from the refrigerant circuit 7 by means of the valve device 27, in particular by means of the valve 28, and in the first switching state, the branch Z4 and thereby the outlet A2 are fluidically separated from the refrigerant circuit 7 by means of the valve device 27, in particular by means of the valve 29, so that in the first switching state no refrigerant can flow from the refrigerant circuit 7 from the connection point V3 via the heat accumulator 17 to the connection point V4 or vice versa.

In the second switching state, the inlet E2 is fluidically connected to the refrigerant circuit 7 via the branch Z3 and in this case also via the valve device 27, in particular via the valve 28, at the connection point V3, and in the second switching state, the outlet A2 is fluidically connected to the refrigerant circuit 7 via the branch Z4 and in this case also via the valve device 27, in particular via the valve 29, at the connection point V4. In the second switching state, the branch Z2 and thus the outlet A1 are fluidically separated from the refrigerant circuit 7 by means of the valve device 27, in particular by means of the valve 28. separated, so that in the second switching state no refrigerant can flow from the refrigerant circuit 7 from the connection point V1 via the heat accumulator 17 to the connection point V2 or vice versa.

The tempering device 6 comprises in the 1 The embodiment shown also includes a collector 8, which is arranged downstream of the mixing point M and upstream of the refrigerant compressor 11, in particular the compressor line 9, in the refrigerant circuit 7. For example, a liquid phase and a vapor or gaseous phase of the refrigerant can be accommodated in the collector 8, in particular simultaneously, and/or, for example, the liquid phase can be separated from the vaporous phase of the refrigerant in the collector 8 by means of the collector 8.

The previous and following arrangements of the components, such as the refrigerant compressor 11, the condenser 14, the expansion valve 15, the expansion valve 18, the mixing point M and the connection points V1, V2, V3 and V4 in the refrigerant circuit 7, described as “upstream” and “downstream”, refer to a flow direction of the refrigerant, also referred to as the operating direction, which flows through the refrigerant circuit 7 and thus through the components mentioned in the first switching state and in the second switching state. In other words, the refrigerant flows in the operating direction through the refrigerant circuit 7 and thus through the components mentioned when the refrigerant is conveyed through the refrigerant circuit 7 by means of the refrigerant compressor 11, while the valve device 27 is optionally in the first switching state or in the second switching state. The operating direction is, for example, in 1 to 3 illustrated by arrows 10.

6 shows a phase diagram of the refrigerant, for example R1234yf, where the 6 The phase diagram shown illustrates operation of the temperature control device 6 without the heat accumulator 17. As usual, the enthalpy of the coolant, in particular the specific enthalpy, is plotted or indicated on the abscissa 20 of the phase diagram, in particular in kilojoules per kilogram. As usual, the pressure of the coolant, in particular in bar, is plotted or indicated on the ordinate 21 of the phase diagram, for example logarithmically. The dew line of the coolant 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 6 shown phase diagram 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 6 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, thus via the compressor branch 9 and the condenser branch 12, and a second thermodynamic cycle, designed as a second triangular process, takes place via points 1, 2 and 5, thus via the compressor branch and the bypass branch 16. The triangular processes, which are also simply referred to as processes, are parallel, whereby none of the triangular processes is self-contained. It is desirable that point 1 is related to the 6 shown phase diagram 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, in particular in the first switching state, preferably also the third 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 or the total mass flow and the third partial mass flow are mixed or blended with one another by means of the expansion valves 15 and 18 and, for example, also by means of a third expansion valve 30, are adjusted such that the enthalpy of the refrigerant at or in the point 1 relative to the in 6 shown phase diagram is safely or stably to the right of the dew line 22. The previous and following statements on the expansion valves 15 and 18 can also be easily transferred to the expansion valve 30. It can be seen that the temperature control device 6 has the third expansion valve 30, which in the first switching state is arranged downstream of the first connection point V1 and upstream of the second connection point V2 and thereby downstream of the heat accumulator 17 and upstream of the second connection point V2. By means of the third expansion valve 30, the third partial mass flow flowing through the heat accumulator 17 in the first switching state is or will be adjusted, that is to say varied and thus changed. For example, the third expansion valve 30 has a The third flow cross-section can be adjusted, i.e. changed or varied, by controlling the expansion valve 30, which can be controlled or is controlled by the electronic computing device 19, in particular as a function of the determined pressures and as a function of the determined temperatures. For this purpose, the third expansion valve 30 comprises, for example, a third, in particular electrically operated, actuator, by means of which the third flow cross-section can be adjusted, i.e. changed, by controlling the expansion valve 30. By adjusting the first partial mass flow, the second partial mass flow and the third partial mass flow, a total mass flow from the partial mass flows, i.e. from the first partial mass flow, the second partial mass flow and the third partial mass flow, can be adjusted, in particular by introducing the third partial mass flow into the refrigerant circuit 7 and thus into the total mass flow, i.e. into the first partial mass flow and into the second partial mass flow, and mixing it with the first partial mass flow and with the second partial mass flow or the total mass flow in the first switching state at the connection point V2. It is therefore desirable that the first partial mass flow, the second partial mass flow and the third 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, 18 and 30 in such a way that the enthalpy of the refrigerant at or in the point 1 relative to the 6 shown phase diagram is safely or stably located 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 6 The phase diagram shown lies safely to the right of the dew line 22, which is also called stabilizing stabilization.

Out of 6 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. In addition, for example, the refrigerant has the same pressure, in particular the same first pressure, at or in points 1, 4 and 5. In 6 a sixth point 31 illustrates the enthalpy of the refrigerant associated with the first pressure and lying on the dew line 22 of the refrigerant. The enthalpy of the refrigerant associated with the first pressure and lying on the dew line 22 of the refrigerant, illustrated by point 31, is also referred to as the dew line enthalpy.

By using the heat accumulator 17 and by the fact that the heat accumulator 17 can optionally absorb heat from the coolant, in particular in the first switching state, or can release heat stored in the heat accumulator 17 to the coolant, in particular in the second switching state, the temperatures and thus the enthalpy of the coolant can be influenced, in particular changed, in a particularly needs-based and advantageous manner, without having to operate the coolant compressor 11 excessively differently. In other words, the coolant compressor 11 can be operated at a particularly efficient operating point, in particular at the same efficient operating point, in order to be able to operate or supply the condenser with different outputs.

Out of 1 it can be seen that the temperature control device 6 has, for example, a check valve 32 which, in the first switching state, is arranged in series with the expansion valve 30 and in series with the heat accumulator 17 such that the check valve 32 is arranged downstream of the expansion valve 30 or downstream of the heat accumulator 17 and upstream of the connection point V2. The check valve 32 is designed to close automatically in the direction of the heat accumulator 17 and thus automatically prevent a flow of the coolant from the connection point V2 through the check valve 32 to the heat accumulator 17. In addition, the check valve 32 is designed to open automatically in the direction of the connection point V2 and thus automatically allow a flow of the coolant from the heat accumulator 17 through the check valve 32 to the connection point V2. This makes it possible to avoid an undesirable backflow of the coolant from the connection point V2 to the heat accumulator 17. Preferably, the refrigerant compressor 11 is an electric refrigerant compressor, which is also referred to as eKMV.

In 2 Arrows 33 show a first flow direction in which the refrigerant flows through the heat accumulator 17 and also through the expansion valve 30 when the refrigerant in the first switching state of the valve device 27 by means of the refrigerant compressor 11 and is thereby conveyed through the heat accumulator 17 and through the expansion valve 30 and in particular also through the condenser branch 12 and the bypass branch 16.

In 3 Arrows 34 illustrate a third flow direction in which the coolant flows through the heat accumulator 17 when, in the second switching state of the valve device 27, the coolant is conveyed by means of the coolant compressor 11 through the heat accumulator 17 and in particular also through the condenser branch 12 and through the bypass branch 16. Thus, in the first switching state of the valve device 27, the coolant flows in the first flow direction from the inlet E1 to the outlet A1, and in the second switching state, the coolant flows in the second flow direction from the inlet E2 to the outlet A2. The inputs E1 and E2 and the outputs A1 and A2 are connections of the heat accumulator 17 or are formed by connections of the heat accumulator 17, wherein in the first switching state a first of the connections is designed or functions as the input E1 and a second of the connections as the output A1, and wherein in the second switching state of the valve device 27 a third of the connections is designed or functions as the input E2 and a fourth of the connections as the output A2.

In order to realize particularly robust operation of the temperature control device 6 and in particular to be able to protect the refrigerant compressor 11 from undesirable damage, the temperature control device 6 has an additional pump 39 provided in addition to the refrigerant compressor 11, which is designed in particular as an electric pump. The additional pump 39 can be used to pump the refrigerant through the heat accumulator 17 while the refrigerant compressor 11 is deactivated. The condenser branch 12 and the bypass branch 16 are also referred to collectively as delivery branches, wherein the additional pump 39 can be used to pump the refrigerant through the heat accumulator 17 and, for example, also through at least or exactly one of the delivery branches, in particular through the bypass branch 16, while the refrigerant compressor 11 is deactivated.

The valve device 27 is in a 4 shown, third switching state, so that the valve device 27 can be switched between the first switching state, the second switching state and the third switching state, in particular by controlling the valve device 27. The valve device 27 comprises the valves 28 and 29 and a third valve 35 and a fourth valve 36. The valves 35 and 36 are designed, for example, as three-/two-way valves. In particular, the additional pump 39 is arranged in a pump branch 37, also referred to as a pump train, which is connected, for example, in particular via the valves 28 and 35, to the refrigerant circuit 7 and, in particular via the valve 36, to one of the second Z1, Z2, Z3, Z4, in particular to the branch Z2.

In the third switching state, the additional pump 39 and thus, for example, the pump branch 37 are connected to the refrigerant circuit 7 and to the heat accumulator 17, in particular to the branch Z2, by means of the valve device 27 in such a way that in the third switching state, the heat accumulator 17 and the additional pump 39 connected in series with the heat accumulator 17 in the third switching state are fluidically connected to the refrigerant circuit at a tapping point AS arranged upstream of the refrigerant compressor 11 in the refrigerant circuit 7 with respect to the operating direction, which is arranged in the refrigerant circuit 7 downstream of the first expansion valve 15 and/or downstream of the second expansion valve 18 with respect to the operating direction, and at an inlet point ES arranged downstream of the refrigerant compressor 11, upstream of the condenser branch 12 and upstream of the bypass branch 16 in the refrigerant circuit 7 with respect to the operating direction, whereby by means of the additional pump 39 in the third switching state, the refrigerant can be conveyed from the tapping point AS to the inlet point ES, bypassing the refrigerant compressor 11, and can thus be conveyed through the heat accumulator 17, bypassing the refrigerant compressor 11, while the refrigerant compressor 11 is deactivated.

For example, in the third switching state of the valve device 27, the heat accumulator 17 and the additional pump 39, which is fluidically connected in series with the heat accumulator 17 in the third switching state, are connected in series with the condenser branch 12 and/or in series with the bypass branch 16.

In 4 , in which the third switching state of the valve device 27 is shown, a second flow direction is illustrated by arrows 38, in which the coolant, which is conveyed by means of the additional pump 39, flows through the heat accumulator 17 and also through the additional pump 39 and in the present case through the bypass line 16 and the expansion valve 18. It can be seen that the second flow direction illustrated by arrows 38, in which in the third switching state the coolant conveyed by means of the additional pump 39 flows through the heat accumulator 17, which in 2 indicated by arrows 33 illustrated first flow direction, in which in the first switching state the refrigerant conveyed by means of the refrigerant compressor 11 flows through the heat accumulator 17. If in the first switching state the refrigerant conveyed by means of the refrigerant compressor 11 flows in the first flow direction from the inlet E1 to the outlet A1, that is to say from the first connection to the second connection of the heat accumulator 17, then in the third switching state the refrigerant conveyed by means of the additional pump 39 flows in the second flow direction opposite to the first flow direction from the outlet A1 to the inlet E2, that is to say from the second connection to the first connection and thereby through the heat accumulator 17. In or due to the third switching state of the valve device 27 and due to the fact that in the third switching state of the valve device 27 the coolant is conveyed through the heat accumulator 17 by means of the additional pump 39, the coolant flowing through the heat accumulator 17 and flowing from the outlet A1 to the inlet E1 can be heated by means of the heat accumulator 17, i.e. by means of heat stored in the heat accumulator 17, without operating the coolant compressor 11. Thus, in the third switching state it is provided that the coolant is conveyed via the outlet A1 to the heat accumulator 17 by means of the additional pump 39, is conveyed from the outlet A1 and the inlet E1 and is thus conveyed through the heat accumulator 17 and is conveyed away from the heat accumulator 17 via the inlet E1, in particular while the coolant compressor 11 is deactivated.

In the embodiment shown in the figures, it is provided that the tapping point AS coincides with the connection point V3. In addition, it is provided here that the introduction point ES coincides with the connection point V1. It can also be seen that in the third switching state at the tapping point AS at least part of the coolant, in particular all of the coolant, is branched off from the coolant circuit 7 and introduced into the pump branch 37, also referred to as the pump line, and thus led to the pump 35, and in the third switching state the coolant flowing through the pump branch 37 and thus the additional pump 39 and also the heat accumulator 17 is (again) introduced into the coolant circuit 7 at the introduction point ES and in the process is led out in particular from the branch Z1. It can also be seen that in the first switching state the coolant flows in the first flow direction through the branch Z2 and through the branch Z1. In the third switching state, the coolant flows in the second flow direction opposite to the first flow direction through the branch Z2 and the branch Z1. In relation to the first flow direction, in the first switching state the expansion valve 30 is arranged downstream of the connection point V1 and upstream of the connection point V2 and thereby downstream of the heat accumulator 17 and upstream of the connection point V2. In relation to the second flow direction, in the third switching state the expansion valve 30 is arranged downstream of the tap point AS and thereby downstream of the connection point V3 and upstream of the inlet point ES and thereby upstream of the connection point V1, in particular such that in relation to the second flow direction in the third switching state the expansion valve 30 is arranged downstream of the tap point AS or downstream of the connection point V3 and upstream of the heat accumulator 17.

In the figures, parts of the temperature control device 6 through which the coolant does not flow are illustrated by dashed lines, and parts of the temperature control device 6 through which the coolant flows are illustrated by solid lines. It can be seen that in the first switching state and in the second switching state the coolant bypasses the additional pump 39, and therefore does not flow through the additional pump 39.

Finally, 5 a fourth switching state of the valve device 27, which can thus be switched to the fourth switching state. Thus, the valve device 27 can be switched between the first switching state, the second switching state, the third switching state and the fourth switching state, in particular by controlling the valve device 27. From 5 it can be seen that in the fourth switching state, the heat accumulator 17 is fluidically separated from the refrigerant circuit 7 by means of the valve device 27. It is also provided that in the fourth switching state, the additional pump 39 is fluidically separated from the refrigerant circuit 7 by means of the valve device 27. If the refrigerant is thus conveyed by means of the refrigerant compressor 11 in the fourth switching state of the valve device 27, the refrigerant flows through the refrigerant circuit 7 and thereby through the compressor branch 9, the condenser branch 12 and the bypass branch 16 without flowing through the heat accumulator 17, the expansion valve 30 or the additional pump 39. As a result, the fourth switching state of the valve device 27 enables, for example, the operation of the temperature control device 6 without the heat accumulator 17, that is to say with the heat accumulator 17 decoupled from the refrigerant circuit 7 and thus switched off.

list of reference symbols

1

Point

2

Point

3

Point

4

Point

5

Point

6

tempering device

7

refrigerant circuit

8

collectors

9

compressor train

10

Arrow

11

refrigerant compressor

12

capacitor bank

14

capacitor

15

first expansion valve

16

bypass line

17

heat storage

18

second expansion valve

19

electronic computing device

20

abscissa

21

ordinate

22

dew line

23

Arrow

24

Arrow

25

Arrow

26

Arrow

27

valve device

28

valve

29

valve

30

expansion valve

31

Point

32

check valve

33

Arrow

34

Arrow

35

valve

36

valve

37

pump branch

38

Arrow

39

additional pump

AWAY

exit area

AS

tap point

A1

Exit

A2

Exit

D1

enthalpy difference

D2

enthalpy difference

EB

entrance area

IT

discharge point

E1

Entrance

E2

Entrance

A

junction

M

mixing point

V1

first connection point

V2

second connection point

V3

third connection point

V4

fourth connection point

S1

sensor device

S2

sensor device

S3

sensor device

Z1

branch

Z2

branch

Z3

branch

Z4

branch

QUOTES INCLUDED IN THE DESCRIPTION

This list of documents listed by the applicant was generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA accepts no liability for any errors or omissions.

Cited patent literature

• JP 5861495 B2 [0002]
• EP 2265453 B1 [0002]
• DE 60320060 T2 [0002]

Claims (14)

Temperature control device (6) for controlling the temperature of at least one part of a motor vehicle, with: - a refrigerant circuit (7) through which a refrigerant flows, which has: o a compressor line (9) through which the refrigerant can flow, in which a refrigerant compressor (11) is arranged, by means of which the refrigerant is to be conveyed and compressed; o a condenser line (12) connected in series with the compressor line (9) and through which a first partial mass flow of the refrigerant can flow, in which a first expansion valve (15) by means of which the first partial mass flow can be adjusted and expanded, and a condenser (14) by means of which the first partial mass flow can be condensed are arranged; o 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 thus mixed with one another, - a heat accumulator (17) designed to store heat, which has: o an inlet area (EB) via which the coolant can be fed to the heat accumulator (17) so that heat from the coolant fed to the heat accumulator (17) via the inlet area (EB) can be stored in the heat accumulator (17) or heat from the heat accumulator (17) can be transferred to the coolant fed to the heat accumulator via the inlet area (EB); and o an outlet area (AB) via which the coolant fed to the heat accumulator (17) via the inlet area (EB) can be discharged from the heat accumulator (17); - a valve device (27) which can be switched between: o a first switching state in which the heat accumulator (17) is fluidically connected to the refrigerant circuit (7) at a first connection point (V1) arranged downstream of the refrigerant compressor (11), upstream of the condenser branch (12) and upstream of the bypass branch (16) in the refrigerant circuit (7) and at a second connection point (V) arranged upstream of the refrigerant compressor (11) in the refrigerant circuit (7), which is arranged in the refrigerant circuit (7) downstream of the first expansion valve (15) and/or downstream of the second expansion valve (18), whereby at least part of the refrigerant compressed by means of the refrigerant compressor (11) can be fed to the heat accumulator (17) via the inlet region (EB) from the first connection point (V1) and which can be fed via the outlet region (AB) from the heat accumulator (17) discharged refrigerant can be introduced into the refrigerant circuit (7) at the second connection point (V2); and o a second switching state in which the heat accumulator (17) is fluidically connected to the refrigerant circuit (7) at a third connection point (V) arranged upstream of the refrigerant compressor (11) in the refrigerant circuit (7), which is arranged in the refrigerant circuit (7) downstream of the first expansion valve (15) and/or downstream of the second expansion valve (18), and at a fourth connection point (V4) arranged downstream of the third connection point (V3) and upstream of the refrigerant compressor (11) in the refrigerant circuit (7), whereby at least part of the total mass flow can be supplied to the heat accumulator (17) via the inlet region (EB) from the third connection point (V3) and the refrigerant discharged from the heat accumulator (17) via the outlet region (AB) can be introduced into the refrigerant circuit (7) at the fourth connection point (V4); and - an additional pump (39) provided in addition to the refrigerant compressor (11), by means of which the refrigerant can be pumped through the heat accumulator (17) while the refrigerant compressor (11) is deactivated. Tempering device (6) according to claim 1 , characterized in that the valve device (27) can be switched to a third switching state, in which the heat accumulator (17) and the additional pump (39) connected in series with the heat accumulator (17) in the third switching state are fluidically connected to the refrigerant circuit (7) at a tapping point (AS) arranged upstream of the refrigerant compressor (11) in the refrigerant circuit (7), which is arranged in the refrigerant circuit (7) downstream of the first expansion valve (15) and/or downstream of the second expansion valve (18), and at an inlet point (ES) arranged downstream of the refrigerant compressor (11), upstream of the condenser branch (12) and upstream of the bypass branch (16) in the refrigerant circuit (7), whereby the refrigerant is bypassed by means of the additional pump (39) from the tapping point (AS) to the inlet point (ES) and can thus be conveyed through the heat accumulator (17) bypassing the refrigerant compressor (11) while the refrigerant compressor (11) is deactivated. Tempering device (6) according to claim 2 , characterized in that the tapping point (AS) coincides with the third connection point (V3). Tempering device (6) according to claim 2 or 3 , characterized in that the inlet point (ES) coincides with the first connection point (V1). Temperature control device (6) according to one of the preceding claims, characterized in that in the first switching state and in the second switching state the refrigerant can be conveyed by means of the refrigerant compressor (11) bypassing the additional pump (39) via the inlet area (EB) to the heat accumulator (17) and can be conveyed away from the heat accumulator via the outlet area (AB). Tempering device (6) according to one of the preceding claims, characterized in that the heat accumulator (17) is designed as a latent heat accumulator which has at least one phase change material for storing the heat. Tempering device (6) according to claim 6 , characterized in that the phase change material has a melting temperature which lies in a range from 50 degrees Celsius to 90 degrees Celsius inclusive. Tempering device (6) according to claim 7 , characterized in that the melting temperature is in a range from 75 degrees Celsius to 90 degrees Celsius inclusive. Tempering device (6) according to claim 8 , characterized in that the melting temperature is in a range from 75 degrees Celsius to 80 degrees Celsius inclusive. Tempering device (6) according to claim 7 , characterized in that the melting temperature is in a range from 50 degrees Celsius to 80 degrees Celsius inclusive. Temperature control device (6) according to one of the preceding claims, characterized in that in the first switching state, a third expansion valve (30), by means of which a third partial mass flow of the coolant, which in the first switching state is supplied to the heat accumulator (17) via the inlet region (17) and flows through the heat accumulator (17), can be adjusted and expanded, is connected in series to the heat accumulator (17) in such a way that in the first switching state the third expansion valve (30) is arranged downstream of the first connection point (V1) and upstream of the second connection point (V2). Tempering device (6) according to claim 11 , characterized in that in the first switching state the third expansion valve (30) is connected in series with the heat accumulator (17) such that in the first switching state the third expansion valve (30) is arranged downstream of the heat accumulator (17) and upstream of the second connection point (V2). Method for operating a tempering device (6) according to one of the preceding claims. Motor vehicle, with at least one temperature control device (6) according to one of the Claims 1 until 12 .

Images