Temperature control device for controlling the temperature of at least one partial range of a motorized vehicle.

Abstract

To enable efficient operation of the temperature control device. [Solution] A refrigerant circuit 7 comprising a compressor train 9 in which a refrigerant compressor 11 is located, a condenser train 12 in which a first expansion valve 15 and a condenser 14 are located, a bypass train 16 in which a second expansion valve 18 is located, and a mixing point M, A heat storage unit 17 having an inlet range EB and an outlet range AB, A valve device 27 is provided that can switch between a first switching state, in which the refrigerant circuit 7 is connected at the first connection point V1 and the second connection point V2, thereby enabling the supply of refrigerant to the heat storage unit 17 and the introduction of refrigerant to the refrigerant circuit 7 at the second connection point V2, and a second switching state, in which the refrigerant circuit 7 is connected at the third connection point V3 and the fourth connection point V4, thereby enabling the supply of refrigerant to the heat storage unit 17 and the introduction of refrigerant to the refrigerant circuit 7 at the fourth connection point V4.

Description

Technical Field

[0001] The present invention relates to a temperature control device for temperature control of at least one partial range of a vehicle with a prime mover. Furthermore, the present invention relates to a method for operating such a temperature control device. In addition, the present invention relates to a vehicle with a prime mover having at least one such temperature control device.

Background Art

[0002] Patent Document 1 discloses a temperature control device for a vehicle. Furthermore, it is recognized from Patent Document 2 that a cooling device for cooling an assembly that is susceptible to the temperature of a vehicle with a prime mover is known. In addition, Patent Document 3 discloses a method for operating a cooling system.

Prior Art Documents

Patent Documents

[0003]

Patent Document 1

Patent Document 2

Patent Document 3

Summary of the Invention

Problems to be Solved by the Invention

[0004] An object of the present invention is to obtain a temperature control device for temperature control of at least one partial range of a vehicle with a prime mover, a method for operating such a temperature control device, and a vehicle with a prime mover having at least one such temperature control device, such that particularly efficient operation of the temperature control device is possible.

Means for Solving the Problems

[0005] (9) The problem is solved by the present invention with a temperature control device having the features of claim 1, a method having the features of claim 9, and a motorized vehicle having the features of claim 10. The advantageous configurations of the present invention are the subject of the dependent claims.

[0006] A first aspect of the present invention relates to a temperature control device for temperature-controlled, i.e., cooling and / or heating, at least one partial area of ​​a motorized vehicle, also simply called a vehicle. This means that a motorized vehicle, also simply called a vehicle, preferably formed as an automobile, particularly a passenger car, is equipped with a temperature control device capable of temperature-controlled, i.e., cooling and / or heating at least the aforementioned partial area in its fully manufactured state. In particular, the method of operating the temperature control device is such that at least a partial area of ​​the motorized vehicle is temperature-controlled, i.e., cooled and / or heated using the temperature control device. For example, the partial area is or includes the interior space of the motorized vehicle, also called the passenger compartment or cabin, in which a person, such as the driver of the motorized vehicle, may reside while the motorized vehicle is in motion. Alternatively, or in addition to the above, the partial area may include, for example, the electrical energy storage unit of the motorized vehicle. Preferably, the electrical energy storage unit, which is capable of or stores electrical energy particularly electrochemically, is a high-voltage component, and its voltage, particularly the operating voltage or rated voltage, is preferably greater than 50 volts, particularly greater than 60 volts, and very preferably several hundred volts. Thus, the motorized vehicle is, for example, a hybrid vehicle or an electric vehicle, particularly a battery electric vehicle (BEV). The motorized vehicle includes, for example, at least one electromachine capable of driving the motorized vehicle specifically electrically only. Preferably, the electromachine is a high-voltage component, and its voltage, particularly the operating voltage or rated voltage, is preferably greater than 50 volts, particularly greater than 60 volts, and very preferably several hundred volts. For example, the electromachine can be supplied with electrical energy stored in the electrical energy storage unit, thereby enabling the electromachine to operate as an electric motor capable of motorizing, and therefore driving the motorized vehicle specifically electrically only.

[0007] The temperature control device includes a refrigerant circuit, also called a circuit or refrigerant circulation path, through which the refrigerant can flow, and in particular, through which the refrigerant flows in this method. The refrigerant circuit includes a compressor train, also called a compressor branch path, which is also called a train or first branch path. The refrigerant can flow through the compressor train, or flows through it. The refrigerant circuit also includes a refrigerant compressor, also called a compressor, which is located in the compressor train. The refrigerant can be transported and compressed using the refrigerant compressor. In other words, the refrigerant compressor can transport and compress the refrigerant. Therefore, for example, in this method, the refrigerant is transported and compressed using the refrigerant compressor.

[0008] The refrigerant circuit also includes a condenser train connected in series with the compressor train, through which a first partial mass flow rate of refrigerant can pass. This condenser train is also called a second train or second branch. For example, the condenser train branches off from the compressor train, particularly at the first branch point. The condenser train is equipped with a first expansion valve, which allows for adjustment and expansion of the first partial mass flow rate. Therefore, for example, in this method, the first partial mass flow rate is expanded using the first expansion valve. Consequently, it is possible to set multiple different values ​​for the first partial mass flow rate using the first expansion valve, thus allowing the first partial mass flow rate to change. In addition, the condenser train is equipped with a condenser, which allows for condensation of the first partial mass flow rate to be tailored to a specific purpose. Therefore, for example, in this method, the first partial mass flow rate is condensed using the condenser to be tailored to a specific purpose. The first partial mass flow rate can be cooled, or is cooled, by condensation of the first partial mass flow rate.

[0009] The refrigerant circuit also includes a bypass train, which is connected in series with the compressor train and in parallel with the condenser train in a fluid-technical manner, thereby allowing a second partial mass flow rate of the refrigerant to pass through it. The bypass train is also called a third train or third branch. Therefore, for example, in this method, the second partial mass flow rate passes through the bypass train. For example, the bypass train branches off from the compressor train, particularly at a second branch point. The branch points can coincide and therefore be formed by one overall branch point, or can be located at one overall branch point, or the branch points are spaced apart from each other, particularly in the direction of refrigerant flow through the refrigerant circuit. In particular, for example, in this method, the second partial mass flow rate passes through the bypass train. A second expansion valve is provided in the bypass train, which can be used to adjust and expand the second partial mass flow rate. Therefore, in particular, in this method, the second partial mass flow rate is expanded using a second expansion valve. The feature that the second partial mass flow rate can be adjusted using the second expansion valve means that it is possible to adjust (set) multiple different values ​​of the second partial mass flow rate using the second expansion valve, thereby making it possible to change, i.e., modify, the second partial mass flow rate. The first or second partial mass flow rate can be adjusted by each first or second expansion valve, in particular by adjusting each flow cross-section of each expansion valve through which the first or second partial mass flow rate can flow, that is, by adjusting different values ​​of each flow cross-section.

[0010] A first partial mass flow rate is passable through or passes through a first expansion valve, and a second partial mass flow rate is passable through or passes through a second expansion valve. A compressor flow formed by the refrigerant, for example, the mass flow rate of the refrigerant, is passable through or passes through the refrigerant compressor and, for example, the compressor train, i.e., at least a portion of the compressor train. The compressor flow includes at least a first partial mass flow rate and a second partial mass flow rate, and is thus formed by at least a first partial mass flow rate and a second partial mass flow rate. In addition, a second partial mass flow rate is passable through or passes through a condenser. The condenser is a heat exchanger that is passable, operated, or functions as the condenser, for example, in at least the operation of a temperature control device, and particularly in at least the operation of a heat pump. For example, a fluid provided in addition to the refrigerant is passable through and / or can bypass the condenser. For example, heat can be transferred from the refrigerant to the fluid via the condenser, thereby making it possible to cool the refrigerant and heat the fluid, particularly in the above operation. Therefore, it is possible to utilize the heat contained in the refrigerant to heat the fluid. It is possible to supply a fluid to a partial range, for example, in order to heat a partial range using the fluid, particularly the heat transferred from the refrigerant to the fluid via a condenser, thereby controlling the temperature. Generally speaking, for example, a partial range can be controlled, especially heated, using the fluid, particularly the heat contained in the fluid transferred from the refrigerant to the fluid via a condenser. For example, the fluid is a gas, particularly air, that is introduced or can be introduced into a partial range, particularly the aforementioned internal space, in order to control, especially heat, the internal space using the fluid. Furthermore, the fluid may also be a liquid. For example, it is possible to control, especially heat, an electrical energy storage unit using the fluid. For this purpose, for example, the fluid is supplied to the electrical energy storage unit. In particular, the above operation is, for example, a heat pump operation.

[0011] The heat transferred from the refrigerant to the fluid via the condenser can be transferred, for example, from the fluid to the electrical energy storage unit to heat the electrical energy storage unit and thus regulate its temperature. The heat that can be transferred or is transferred from the refrigerant to the fluid via the condenser originates, for example, at least primarily from, or solely from, the refrigerant compressor, or is generated, at least primarily from, or solely from, the refrigerant compressor, or introduced into the refrigerant by the refrigerant compressor, which compresses the refrigerant and heats it therein. Therefore, the refrigerant compressor can be used as a heat source to heat the refrigerant, particularly the fluid via the condenser, and subsequently heat a portion of it.

[0012] Furthermore, the bypass train and the condenser train merge, particularly at just one mixing point, thereby fluidically connecting them to each other. At the mixing point, the first partial mass flow rate and the second partial mass flow rate can merge with the total mass flow rate, or are merged, and at the mixing point, the first partial mass flow rate and the second partial mass flow rate can be mixed with each other, or are mixed, by being merged with the total mass flow rate at the mixing point. Therefore, the compressor flow flowing through the refrigerant compressor includes at least the total mass flow rate or only the total mass flow rate. In particular, in the first operating state of the temperature control device, the compressor flow may include only the total mass flow rate, and therefore only the first partial mass flow rate and the second partial mass flow rate, and thus may be formed by the total mass flow rate alone. In the second operating state of the temperature control device, the compressor flow includes, for example, a total mass flow rate and at least one or just one other partial mass flow rates of the refrigerant. Therefore, in the second operating state of the compressor flow, the compressor flow is formed in particular by a first partial mass flow rate, a second partial mass flow rate, and at least one or just one other partial mass flow rate of the refrigerant. The first partial mass flow rate and the second partial mass flow rate merge at a mixing point, thereby mixing with each other or being able to mix, so that the first partial mass flow rate and the second partial mass flow rate form or produce a total mass flow rate, which can be introduced, and thus flowed into, the compressor train, and in this case, the refrigerant compressor. Because the first partial mass flow rate and the second partial mass flow rate merge and thus mix with each other, so that the first partial mass flow rate and the second partial mass flow rate produce or form a total mass flow rate, the first partial mass flow rate and the second partial mass flow rate are, in themselves, less than the total mass flow rate and the compressor flow. In addition, other partial mass flow rates, when viewed in themselves, are smaller than the compressor flow and, for example, the total mass flow rate.

[0013] For example, the first partial mass flow rate is configured to branch off from the compressor flow or another mass flow rate of refrigerant branched off from the compressor flow at, for example, the first branching point. Furthermore, the second partial mass flow rate is configured to branch off from the compressor flow or another mass flow rate of refrigerant branched off from the compressor flow, particularly at the second branching point. When branching points merge, the compressor flow or another mass flow rate may branch off into the first partial mass flow rate and the second partial mass flow rate at the overall branching point, and thus be divided.

[0014] In the method of operating the temperature control device, the first pressure and first temperature of the refrigerant, particularly the compressor flow through the refrigerant compressor, are determined in the compressor train, upstream of the refrigerant compressor and downstream of the mixing point, for example, using the electronic computing device of the temperature control device, particularly of a motorized vehicle. The first pressure of the refrigerant, particularly the compressor flow, is understood to be the pressure of the refrigerant, particularly the compressor flow, where the first pressure occurs at a first pressure point, which is located in the compressor train, upstream of the refrigerant compressor and downstream of the mixing point. The first temperature of the refrigerant, particularly the compressor flow, is understood to be the temperature of the refrigerant, particularly the compressor flow, where the first temperature occurs at a first temperature point, which is located in the compressor train, upstream of the refrigerant compressor and downstream of the mixing point. For example, the first pressure point and the first temperature point coincide.

[0015] The second pressure and second temperature of the refrigerant are determined using an electronic computing device downstream of the refrigerant compressor, upstream of the condenser, and upstream of the expansion valve. The second pressure of the refrigerant can be understood as the refrigerant pressure, which arises at second pressure points located downstream of the refrigerant compressor, upstream of the condenser, and upstream of the expansion valve, and these second pressure points are located, for example, in the compressor train, bypass train, or condenser train. Thus, for example, the second pressure is the second pressure of the compressor flow passing through the refrigerant compressor, and the compressor flow has a second pressure, particularly downstream of the refrigerant compressor, upstream of the condenser, and upstream of the expansion valve, especially upstream of branching points, particularly in the compressor train. In the foregoing and following, when referring to the expansion valve, it can be understood as the first expansion valve and the second expansion valve unless otherwise specified. The second temperature of the refrigerant can be understood as the temperature of the refrigerant itself, and this second temperature occurs at second temperature locations located downstream of the refrigerant compressor, upstream of the condenser, and upstream of the expansion valve, and these second temperature locations are located in the compressor train, bypass train, or condenser train. In particular, it is conceivable that the second pressure location and the second temperature location coincide. Therefore, for example, the second temperature is the second temperature of the compressor flow passing through the refrigerant compressor, and the compressor flow has a second temperature, particularly downstream of the refrigerant compressor, upstream of the condenser, and upstream of the expansion valve, and especially upstream of branching points, in the compressor train.

[0016] The third pressure and third temperature of the refrigerant, particularly the first partial mass flow rate, are determined in the condenser train, downstream of the condenser and upstream of the first expansion valve, using an electronic computing device. The third pressure of the refrigerant, particularly the compressor flow, can be understood as the pressure of the refrigerant, particularly the compressor flow, where the third pressure occurs at a third pressure location, which is located in the condenser train, downstream of the condenser and upstream of the first expansion valve. The third temperature of the refrigerant, particularly the first partial mass flow rate, can be understood as the temperature of the refrigerant, particularly the first partial mass flow rate, where the third temperature occurs at a third temperature location, which is located in the condenser train, downstream of the condenser and upstream of the first expansion valve. The third pressure location and the third temperature location may coincide.

[0017] As described above, since the compressor flow can pass through the refrigerant compressor, in this method, for example, the compressor flow passes through the refrigerant compressor and, consequently, at least a portion of the compressor train. The pressure and temperature are determined using an electronic computing device, which will be described in detail later.

[0018] In this method, the expansion valve is controlled (operated) using an electronic computing device depending on a specified temperature and a specified pressure, thereby adjusting (setting) the first and second partial mass flow rates depending on the specified temperature and a specified pressure. In the above and below, when referring to partial mass flow rates, unless otherwise specified, it can be understood as the first and second partial mass flow rates. This means, for example, that by adjusting, i.e., changing the flow cross-section of the expansion valve through the control of the expansion valve, the partial mass flow rates are adjusted, i.e., changed, depending on the specified pressure and a specified temperature, via the expansion valve, i.e., by the control of the expansion valve, using an electronic computing device. Particularly advantageously, this allows adjustment of the ratio between partial mass flow rates, also called the mixing ratio, particularly the ratio between the first and second partial mass flow rates, thereby enabling robust operation of the temperature control device and, subsequently, effective and efficient temperature control. In particular, by adjusting the first and second partial mass flow rates, and thus the mixing ratio, it is possible to prevent the supply of wet vapor or liquid to the refrigerant compressor. In other words, for example, it is possible to prevent the compressor flow obtained by mixing at least the first partial mass flow rate with a second partial mass flow rate, which includes at least the first and second partial mass flow rates and flows through the compressor train, from containing wet vapor or liquid, thereby preventing undesirable damage to the temperature control device. Furthermore, it is possible to achieve particularly advantageous temperature control of a partial range without placing an electric water heater in the refrigerant circuit or in a temperature control circuit through which a fluid can flow, for example, which is additionally provided for temperature control of a partial range. Moreover, since a heat exchanger, also called a cooling device, which can or operates as an evaporator, located in the refrigerant circuit, for example in the temperature control circuit, can be omitted, it is possible to keep the number of parts, and therefore the weight and cost of the temperature control device, particularly small.At the same time, it is possible to adjust the partial mass flow rate and therefore the mixing ratio so that the overall mass flow rate is in a particularly favorable state, especially in the assembly state, such that, for example, the enthalpy of the overall mass flow rate is to the right of the saturated vapor line of the refrigerant formed as, for example, R1234yf in the refrigerant phase diagram, for example, with enthalpy, especially specific enthalpy, plotted on the horizontal axis of the phase diagram and the refrigerant pressure plotted on a logarithmic scale on the vertical axis of the phase diagram.

[0019] To enable particularly efficient operation of a temperature control device, especially a refrigerant compressor, the temperature control device is equipped with a condenser formed to store heat. In other words, heat can be stored using the condenser, i.e., in the condenser. This means, in particular, that heat can be selectively introduced into the condenser and therefore stored in the condenser, or that the condenser can release the heat stored in the condenser. The condenser is equipped with an inlet range through which a refrigerant can be supplied to the condenser, so that heat can be selectively introduced into the condenser from the refrigerant supplied to the condenser via the inlet range, or that heat stored in the condenser can be transferred from the condenser to the refrigerant supplied to the condenser via the inlet range. In particular, since the refrigerant supplied to the heat storage unit via the inlet range can flow through the heat storage unit, heat can be selectively introduced into the heat storage unit from the refrigerant supplied to the heat storage unit via the inlet range and flowing through the heat storage unit, or heat stored in the heat storage unit can be transferred from the heat storage unit to the refrigerant supplied to the heat storage unit via the inlet range and flowing through the heat storage unit.

[0020] Furthermore, the heat storage unit has an outlet area, through which the refrigerant supplied to the heat storage unit via the inlet area and flowing through the heat storage unit can be discharged from the heat storage unit after it has been supplied to the heat storage unit via the inlet area, that is, it can be led out of the heat storage unit. This means, for example, that the refrigerant can flow through the heat storage unit so that it can flow from the inlet area to the outlet area and, at the same time, can flow through the heat storage unit. In other words, the refrigerant flows through the heat storage unit from the inlet area to the outlet area in its path. Therefore, the outlet area is located downstream of the inlet area. Thus, for example, in this method, especially in the above operation, since the refrigerant is supplied to the heat storage unit via the inlet area, the refrigerant flows into the heat storage unit via the inlet area and flows through the heat storage unit, at the same time flows from the inlet area to the outlet area, flows out of the heat storage unit via the outlet area, and is therefore discharged from the heat storage unit. Between the refrigerant flowing through the condenser from the inlet to the outlet, and the condenser, that is, for example, between the refrigerant flowing through the condenser from the inlet to the outlet, and at least one storage element (heat storage element) of the condenser, heat can be exchanged, or is exchanged, so that, selectively, heat is transferred from the refrigerant flowing through the condenser to the condenser, or heat is transferred from the condenser to the refrigerant flowing through the condenser. When heat is transferred from the refrigerant flowing through the condenser to the condenser, the heat transferred from the refrigerant to the condenser is introduced into the condenser and therefore stored in the condenser. This cools the refrigerant. When heat is transferred from the condenser to the refrigerant flowing through the condenser, the refrigerant is heated and the heat is released from the condenser.

[0021] More preferably, the first expansion valve is located downstream of the condenser and particularly upstream of the mixing point in the condensing train. Furthermore, the temperature control device includes a valve device which is switchable between a first switching state and a second switching state. In particular, the valve device can be switched between the first switching state and the second switching state by control (operation) of the valve device. For example, the valve device can be controlled (operated) by supplying electrical energy to the valve device. In other words, for example, the valve device can be controlled (operated) by supplying electrical energy to the valve device. In the first switching state, the accumulator is connected to the refrigerant circuit using a valve device such that, in the first switching state, the accumulator is fluidly connected to the refrigerant circuit at a first connection point located downstream of the refrigerant compressor, upstream of the condenser train and upstream of the bypass train, in the refrigerant circuit, particularly in the compressor train, and at a second connection point located upstream of the refrigerant compressor, in the refrigerant circuit, particularly in the compressor train, downstream of the first expansion valve and / or downstream of the second expansion valve. This allows, in the first switching state, at least a portion of the refrigerant compressed by the refrigerant compressor to be supplied to the accumulator from the first connection point through the inlet range, and the refrigerant discharged from the accumulator through the outlet range to be introduced into the refrigerant circuit at the second connection point. Therefore, for example, in the first switching state, the accumulator is connected to the refrigerant circuit using valve devices such that the accumulator is connected in parallel with the bypass train, in parallel with the condenser train, and in series with the compressor train, in a fluid-technical manner, so that at least a portion of the refrigerant compressed using the refrigerant compressor can be supplied to the accumulator, particularly through the inlet range. Thus, for example, in the first switching state, a third partial mass flow rate of refrigerant can be supplied to the accumulator from the first connection point through the inlet range, and the third partial mass flow rate is formed by or formed by the refrigerant compressed using the refrigerant compressor, i.e., a portion of the refrigerant compressed using the refrigerant compressor. Thus, the third partial mass flow rate is the portion of the refrigerant compressed using the refrigerant compressor that can be supplied to the accumulator through the inlet range in the first switching state.

[0022] At this time, in particular, it is conceivable that the third partial mass flow rate is discharged from the regenerator via the outlet range and introduced into the refrigerant circuit at the second connection point. In particular, since the third partial mass flow rate is the above-mentioned another partial mass flow rate, for example, in the first switching state, the compressor flow includes, for example, the total mass flow rate, particularly only the total mass flow rate and at least or exactly the third partial mass flow rate of the refrigerant. As a result, in the first switching state, the compressor flow is formed by the first partial mass flow rate, the second partial mass flow rate, and the third partial mass flow rate of the refrigerant, particularly only the first partial mass flow rate, the second partial mass flow rate, and the third partial mass flow rate. Therefore, for example, it is possible that the valve device is configured to be in the first switching state in the above-mentioned second operating state.

[0023] In particular, the second connection point can coincide with the mixing point, or the second connection point is arranged particularly downstream of the mixing point in the compressor train. It is also conceivable that the second connection point is arranged in the condenser train or the bypass train at this time upstream of the mixing point. The first connection point can coincide with, for example, the first branch point and / or the second branch point and / or the overall branch point, or the first connection point is spaced apart from the first branch point and / or the second branch point and / or the overall branch point. In particular, in the first switching state, the compressor flow branches into the first partial mass flow rate, the second partial mass flow rate, and the third partial mass flow rate at the first connection point, or in the first switching state, for example, the compressor flow is configured to branch at the first connection point into the third partial mass flow rate and another mass flow rate that branches into the first partial mass flow rate and the second partial mass flow rate, for example, at the overall branch point.

[0024] In the second switching state, in the second switching state, the heat accumulator is arranged upstream of the refrigerant compressor in the refrigerant circuit, particularly in the compressor train, and is fluidly connected to the refrigerant circuit at a third connection point arranged downstream of the first expansion valve and / or downstream of the second expansion valve in the refrigerant circuit by using a valve device. The third connection point may coincide with the mixing point or is preferably arranged downstream of the mixing point.

[0025] In the second switching state, the heat accumulator is connected to the refrigerant circuit by using a valve device such that, in the second switching state, the heat accumulator is fluidly connected to the refrigerant circuit at a fourth connection point arranged downstream of the third connection point and upstream of the refrigerant compressor in the refrigerant circuit, particularly in the compressor train. Thereby, in the second switching state, a part of the total mass flow rate, particularly the entire mass flow rate, can be supplied from the third connection point to the heat accumulator via the inlet range, and the refrigerant discharged from the heat accumulator via the outlet range can be introduced into the refrigerant circuit at the fourth connection point. In particular, it is configured such that the entire total mass flow rate can flow through the third connection point.

[0026] Therefore, for example, in the second switching state, the heat accumulator is fluidly connected to the refrigerant circuit by using a valve device such that the heat accumulator is arranged particularly downstream of the condenser train, downstream of the bypass train, and upstream of the refrigerant compressor. Therefore, for example, in the second switching state, since the compressor flow passing through the refrigerant compressor contains only the total mass flow rate, particularly only the total mass flow rate, in the second switching state, the compressor flow is formed by the first partial mass flow rate and the second partial mass flow rate of the refrigerant, particularly only by the first partial mass flow rate and the second partial mass flow rate. Therefore, for example, it is possible to configure the valve device to be in the second switching state in the above-described first operating state.

[0027] Since the refrigerant compressor compresses the refrigerant and thereby heats it, for example, in the first switching state, the refrigerant compressed using the refrigerant compressor and thereby heated can be supplied to the accumulator, particularly in the form of a third partial mass flow rate, as a result, heat can be transferred from the refrigerant to the accumulator and thus introduced into the accumulator. Thus, in the first switching state, the accumulator is fluidly connected to the high-pressure side of the refrigerant compressor via an inlet range, or the inlet range is also called the high-pressure range, and the refrigerant compressor provides the refrigerant compressed using the refrigerant compressor, either on its high-pressure side or via its high-pressure side. In the second switching state, since the accumulator is fluidly connected to the refrigerant circuit via an inlet range, or the inlet range is at a third connection point, in the second switching state, the refrigerant expanded using a first expansion valve and / or a second expansion valve can be supplied to the accumulator via the inlet range, particularly in the form of a total mass flow rate. Therefore, in the second switching state, the condenser is fluidly connected to the low-pressure side of the refrigerant circuit via the inlet range, or the inlet range is fluidly connected to the low-pressure side of the refrigerant circuit, also called the low-pressure range. Thus, for example, in the second switching state, heat is transferred from the condenser to the refrigerant flowing through the condenser, particularly to the total mass flow rate or compressor flow, thereby heating the refrigerant before it flows through the refrigerant circuit compressor. Because the fourth connection point is located downstream of the third connection point and upstream of the refrigerant compressor, the refrigerant compressor is heated or supplied with heated refrigerant, either by the use of the condenser and, consequently, by the transfer of heat from the condenser to the refrigerant. Thus, the present invention enables particularly efficient operation of the temperature control device. In particular, the present invention makes it possible to operate the refrigerant compressor of the condenser by such particularly electrical power (electricity), so that the refrigerant circuit can operate at an efficient operating point independently of the power requirements of the condenser, i.e., independently of the power to operate the condenser or the power supplied to the condenser.

[0028] For example, in a second operating state of the temperature control device, if the condenser is operated with, or supplied with, such power, the refrigerant compressor needs to be operated with, for example, 2 kilowatts of power without using the condenser, then, by using the condenser, and in the first switching state of the valve device, the refrigerant compressor can be operated with more power than 2 kilowatts, and thereby essentially more effectively, and therefore more efficiently. This is because the excess power of the refrigerant compressor, which is not needed for the operation of the condenser, can be introduced into the condenser as heat. Therefore, for example, in the second operating state, it is possible to operate the refrigerant compressor with 6 kilowatts instead of 2 kilowatts. Of the 6 kilowatts of power of the refrigerant compressor, 2 kilowatts can be used to operate the condenser, and the remaining 4 kilowatts of power of the refrigerant compressor can be used to introduce heat into the condenser. The heat introduced into the condenser can then be used, for example, in the first operating state, to enable particularly efficient operation of the refrigerant compressor even in the first operating state.

[0029] For example, if the condenser is operated with such power, or supplied with such power, in the second operating state of the temperature control device, the refrigerant compressor needs to be operated with, for example, 9 kilowatts of power without using the condenser, then, by using the condenser, and in the second switching state of the valve device, the refrigerant compressor can be operated with less power than 9 kilowatts, and thereby essentially more effectively, and therefore more efficiently. This is because the heat stored in the condenser can be used to heat the refrigerant. Thus, in the second switching state, and therefore for example in the first operating state, the refrigerant can be heated using either the refrigerant compressor or the heat from the condenser. In other words, the heat stored in the condenser, i.e., the condenser introduced into the condenser in the second operating state, can support the refrigerant compressor when heating the refrigerant in the first operating state. Thus, for example, in the first operating state, the refrigerant compressor can be operated with 6 kilowatts instead of 9 kilowatts. The 3 kilowatts of power needed to operate the condenser are compensated for or provided, for example, by heat transfer from a heat accumulator to the refrigerant. This ensures that, when the heat accumulator is not used, and especially when the refrigerant compressor compresses the refrigerant with 9 kilowatts of power alone, the refrigerant has a high enough heat level before being compressed by the refrigerant compressor that the refrigerant has a temperature downstream of the refrigerant compressor, upstream of the bypass train, and upstream of the condenser train, so that the compressed refrigerant has a temperature downstream of the refrigerant compressor, upstream of the bypass train, and upstream of the condenser train. In both operating conditions, it is found that the refrigerant compressor can operate, for example, at 6 kilowatts, and therefore particularly efficiently and effectively, enabling particularly effective and efficient operation of the temperature control device.

[0030] Furthermore, it can be seen that the refrigerant compressor, in the first and second switching states, transports the refrigerant toward the heat accumulator via the inlet range, and particularly transports it away from the heat accumulator via the outlet range, and in this case, it is possible to transport the refrigerant through the heat accumulator.

[0031] In one embodiment of the present invention, in order to achieve particularly efficient operation of the temperature control device, the heat accumulator is configured to be formed as a latent heat accumulator, also called a phase change heat accumulator or PCM (PCM-Phase Change Material) heat accumulator. The latent heat accumulator comprises at least one phase change material that stores heat. Therefore, the phase change material is the storage element (heat storage element) described above.

[0032] At this time, it was found that having a melting temperature in the range of 50 degrees Celsius to 90 degrees Celsius is particularly advantageous for achieving efficient operation.

[0033] In particular, to achieve efficient operation, another configuration of the present invention is such that the melting temperature of the phase change material is in the range of 75 degrees Celsius or more and 90 degrees Celsius or less.

[0034] In another particularly advantageous embodiment of the present invention, the melting temperature is configured to be in the range of 75 degrees Celsius or more and 80 degrees Celsius or less. This makes it possible to ensure particularly efficient operation.

[0035] Another embodiment is characterized in that the melting temperature is in the range of 50 degrees Celsius to 80 degrees Celsius. This allows for particularly efficient and therefore effective operation of the temperature control device.

[0036] In an alternative configuration of the present invention, to enable the temperature control device to operate particularly effectively and therefore efficiently, the temperature control device is provided with a third expansion valve in addition to the first and second expansion valves, the third expansion valve being connected in series with respect to the accumulator such that in a first switching state, preferably with respect to the switching state, and only in the first switching state, the third expansion valve is positioned downstream of the first connection point and upstream of the second connection point in the first switching state. The above-described third partial mass flow rate of the refrigerant flowing through the accumulator in the first switching state can be adjusted and expanded using the third expansion valve. In this case, the above-described and later configurations for the first and second expansion valves can be easily applied to the third expansion valve, and vice versa.

[0037] In another configuration of the present invention, in order to achieve particularly efficient and therefore effective operation of the temperature control device, the third expansion valve is connected in series with the accumulator in the first switching state such that the third expansion valve is located downstream of the accumulator and upstream of the second connection point in the first switching state.

[0038] A second aspect of the present invention relates to a method for operating a temperature control device according to the first aspect of the present invention. The advantages and favorable configurations of the first aspect of the present invention can be considered as advantages and favorable configurations of the second aspect of the present invention, and vice versa.

[0039] A third aspect of the present invention relates to a motorized vehicle, also simply called a vehicle, preferably formed as an automobile, particularly a passenger car, which is equipped with at least one temperature control device according to the first aspect of the present invention.

[0040] Further details of the present invention will become apparent from the following description of preferred embodiments with reference to the relevant figures. [Brief explanation of the drawing]

[0041] [Figure 1]This diagram schematically shows a temperature control device for controlling the temperature of at least one partial range of a motorized vehicle. [Figure 2] This is a diagram illustrating the state of the refrigerant flowing through the refrigerant circuit of a temperature control device, in a method for operating the temperature control device. [Figure 3] This is a schematic diagram of a temperature control device, where the valve mechanism of the temperature control device is in the first switching state. [Figure 4] This is a schematic diagram of the temperature control device, with the valve mechanism in the second switching state. [Modes for carrying out the invention]

[0042] In each figure, identical or functionally identical elements are given the same reference numeral.

[0043] Figure 1 schematically illustrates a temperature control device 6 for a motorized vehicle, also simply called a vehicle, preferably formed as an automobile, particularly a passenger car. In particular, a method for operating the temperature control device 6 will be described based on each figure. Using the temperature control device 6, it is possible to control the temperature, i.e., heat or cool at least a portion of the motorized vehicle. In particular, it is possible to heat the portion. For example, the portion is the interior space of the motorized vehicle, also called the passenger compartment or cabin, or includes such an interior space, and the structure of the interior space, for example, formed as a self-supporting vehicle body, forms or defines the interior space. Therefore, for example, it is possible to control the temperature, particularly heat, of the interior space using the temperature control device 6. For this purpose, the temperature control device 6 is equipped with a refrigerant circuit 7 through which a refrigerant can flow, and the refrigerant flows through the refrigerant circuit 7 when the temperature control device 6 is operating in this method, and therefore in operation according to this method.

[0044] The refrigerant circuit 7 includes a compressor train 9 through which the refrigerant can flow. A refrigerant compressor 11 is located in the compressor train 9, and the refrigerant can be transported and compressed using the refrigerant compressor 11. In the above operation, therefore in this method, for example, the refrigerant is transported and compressed using the refrigerant compressor 11. In particular, at least a portion of the refrigerant compressor 11 and thus the compressor train 9 is passable to the compressor flow formed by the refrigerant, and the compressor flow is the mass flow rate of the refrigerant flowing through the refrigerant compressor 11. For example, the compressor flow is the total mass flow rate (gross mass flow rate) of at least one or only refrigerant formed as the mass flow rate of the refrigerant, or includes such total mass flow rate, which will be explained in more detail below.

[0045] The refrigerant circuit 7 is fluid-technically connected in series with the compressor train 9, and here it branches off from the compressor train 9 at branch point A, thereby providing a condenser train 12 through which a first partial mass flow rate of refrigerant can pass. The condenser train 12 is equipped with a condenser 14, also called a liquefaction device, which can be used to condense or make condensation possible of the first partial mass flow rate, and therefore the refrigerant flowing through the condenser train 12, and thus it can be liquefied or make liquefyable. In addition, the condenser train 12 is equipped with a first expansion valve 15 downstream of the condenser 14, which can be used to adjust the first partial mass flow rate. Furthermore, the first partial mass flow rate, and therefore the refrigerant flowing through the condenser train 12, can be expanded or is expanded using the expansion valve 15.

[0046] The refrigerant circuit 7 also includes a bypass train 16, which is connected in parallel to the condenser train 12 in a fluid-technical manner and in series to the compressor train 9. In this case, the bypass train 16 branches off from the compressor train 9 at branch point A, allowing a second partial mass flow rate of the refrigerant to pass through. Since both the bypass train 16 and the condenser train 12 branch off from the compressor train 9 at branch point A, branch point A is the overall branch point.

[0047] The bypass train 16 is equipped with a second expansion valve 18 in addition to the expansion valve 15, and the second partial mass flow rate can be adjusted using this second expansion valve. In addition, the second partial mass flow rate, and therefore the refrigerant flowing through the bypass train 16, can be expanded using the expansion valve 18 or is expanded. Preferably, in this method, evaporation of the refrigerant using an evaporator does not occur in the compressor train 9, the condenser train 12, and the bypass train 16, and especially in the entire refrigerant circuit 7. The compressor train 9, the condenser train 12, and the bypass train 16 are also called trains. In the embodiments shown in each figure, the trains do not have evaporators for intentional evaporation of the refrigerant.

[0048] The condenser train 12 and the bypass train 16 merge at a single mixing point M of the refrigerant circuit 7, so that at mixing point M, the first partial mass flow rate and the second partial mass flow rate can merge into the total mass flow rate, thereby allowing them to mix with each other. Thus, in this method, they merge and thus mix or blend with each other. The total mass flow rate can be introduced from mixing point M to the compressor train 9, so that it can flow in, so that it can flow through the compressor train 9 and, consequently, the refrigerant compressor 11. In other words, the total mass flow rate can be supplied from mixing point M to the refrigerant compressor 11, so that it can flow through the refrigerant compressor 11. Thus, the compressor flow is at least the total mass flow rate or includes the total mass flow rate. In other words, it is conceivable that the compressor flow includes only the total mass flow rate and is therefore formed only by the total mass flow rate in at least the first operating state of the temperature control device 6. Furthermore, in particular in the second operating state of the temperature control device 6, the compressor flow includes the total mass flow rate of the refrigerant and at least one, or exactly one, other partial mass flow rate, and is therefore formed by the total mass flow rate of the refrigerant and the other partial mass flow rates, in which case it may include only the total mass flow rate and the other partial mass flow rates.

[0049] An electronic computing device 19, particularly schematically illustrated in Figure 1, is used to determine the first pressure and first temperature of the refrigerant, especially the compressor flow, upstream of the refrigerant compressor 11 and downstream of the mixing point M in the compressor train 9. In the embodiment shown in Figure 1, a first sensor device S1 is provided, which is used to measure the first pressure and first temperature of the refrigerant, especially the compressor flow, occurring upstream of the refrigerant compressor 11 and downstream of the mixing point M in the compressor train 9. 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, thereby allowing the electronic computing device 19 to determine the first temperature and the first pressure. In Figure 1, a first point is indicated by reference numeral 1, and this first point is also called the first location. The first point 1 is located downstream of the mixing point M and upstream of the refrigerant compressor 11 in the compressor train 9. For example, the sensor device S1 measures the first pressure and first temperature within or at the first point 1. In other words, for example, the first pressure and first temperature of the refrigerant in the compressor train 9 occur at point 1.

[0050] In this method, the second pressure and second temperature of the refrigerant, particularly the compressor flow, are determined using an electronic computing device 19 downstream of the refrigerant compressor 11, upstream of the condenser 14, and upstream of the expansion valves 15 and 18. In the embodiment shown in Figure 1, a second sensor device S2 is provided, which is used to detect the second pressure of the refrigerant and the second temperature of the refrigerant occurring downstream of the refrigerant compressor 11, upstream of the condenser 14, and upstream of the expansion valves 15 and 18. The sensor device S2 provides, for example, a second signal characterizing the second temperature and the second pressure. For example, the electronic computing device 19 receives the second signal, thereby determining the second pressure and the second temperature. In Figure 1, the second point is indicated by reference numeral 2, and this second point is also called the second location. It can be seen that the first point is located downstream of the mixing point M in the compressor train 9 and upstream of the refrigerant compressor 11. The second point 2 is located downstream of the refrigerant compressor 11, upstream of the condenser 14 and upstream of the expansion valves 15 and 18. For example, the second point can be located at branching point A, or may coincide with branching point A. In this case, the condenser train 12 and the bypass train 16 branch off from the compressor train 9 at branching point A. At this time, for example, the second pressure and second temperature occur at or within the second point 2, and for example, the second sensor device S2 measures the second pressure and second temperature within or at the second point.

[0051] In the condenser train 12, downstream of the condenser 14 and upstream of the first expansion valve 15, the third pressure and third temperature of the refrigerant, particularly the first partial mass flow rate, are determined using an electronic computing device 19, the first expansion valve being located downstream of the condenser 14 and upstream of the mixing point M in the condenser train 12. In the embodiment shown in Figure 1, a third sensor device S3 is provided, which is used to detect the third pressure of the refrigerant occurring downstream of the condenser 14 and upstream of the first expansion valve 15 in the condenser train 12, and the third temperature of the refrigerant occurring downstream of the condenser 14 and upstream of the expansion valve 15 in the condenser train 12. For example, the third sensor device S3 provides a third signal characterizing the third temperature and third pressure. The electronic computing device 19 receives, for example, the third signal, thereby determining the third temperature and third pressure.

[0052] The expansion valves 15 and 18 are controlled (operated) using the electronic computing unit 19, depending on a specified temperature and a specified pressure, thereby adjusting (setting) the first and second partial mass flow rates depending on the specified temperature and a specified pressure. This adjusts the mixing ratio, also called the blending ratio, and according to this mixing ratio, the first and second partial mass flow rates are mixed with each other, or blended, and based on this, the total mass flow rate is obtained. In particular, the mixing ratio is a quotient also called a mixing quotient, or describes such quotient, where the mixing quotient has, for example, the first partial mass flow rate in its numerator and the second partial mass flow rate in its denominator. The first partial mass flow rate is represented, for example, by m1, and the second partial mass flow rate is represented, for example, by m2. The mixing ratio is represented, for example, by Φ. Therefore, for example, the following holds:

[0053]

number

[0054] The expansion valve 15 can be controlled (operated) to adjust, i.e., change, the first flow cross-section of the first expansion valve 15 through which a first partial mass flow rate can pass. For example, the expansion valve 15 is equipped with a first actuator that is electrically operable, and the first flow cross-section can be adjusted using this first actuator. For example, the expansion valve 18 has a second flow cross-section through which a second partial mass flow rate can pass, and this second flow cross-section can be adjusted, i.e., changed by controlling (operating) the expansion valve 18. For example, the expansion valve 18 is equipped with a second actuator that is electrically operable, and the second flow cross-section can be adjusted using this second actuator. In order to adjust the flow cross-section, and therefore the partial mass flow rate and thus the mixing ratio Φ, the electronic computing unit 19 controls the actuators, for example, depending on a specified pressure and depending on a specified temperature.

[0055] In Figure 1, a third point is indicated by reference numeral 3, which is also called the third location. It is conceivable that the third point is located downstream of the condenser 14 and upstream of the expansion valve 15 in the condenser train 12. For example, the third temperature and third pressure occur at or within the third point. For example, a third sensor device S3 measures the third pressure and third temperature at or within the third point. Furthermore, a fourth point is indicated by reference numeral 4 in Figure 1, which is also called the fourth location or is the fourth location. It can be seen that the fourth location, and therefore the fourth point 4, is located in the condenser train 12, and at this time downstream of the expansion valve 15 and upstream of the mixing location M. Furthermore, a fifth point is indicated by reference numeral 5 in Figure 1, which is also called the fifth location or is formed as the fifth location. It can be seen that the fifth point 5 is located downstream of the expansion valve 18 and upstream of the mixing point M in the bypass train 16.

[0056] To enable particularly efficient operation of the temperature control device 6, the temperature control device 6 includes a heat accumulator 17 formed to store heat, which is here formed as a latent heat accumulator and therefore comprises at least one or just one phase change material for storing heat. The heat accumulator 17 has an inlet range EB having at least two or just two inlets, namely a first inlet E1 and a second inlet E2. Furthermore, the heat accumulator 17 has an outlet range AB having at least two or just two outlets, namely a first outlet A1 and a second outlet A2. Since a refrigerant can be supplied to the heat accumulator 17 through the inlet range EB, heat can selectively be stored in the heat accumulator 17 from the refrigerant supplied to the heat accumulator 17 through the inlet range EB and flowing through the heat accumulator 17, or heat can be transferred from the heat accumulator 17 to the refrigerant supplied to the heat accumulator 17 through the inlet range EB and flowing through the heat accumulator 17. The refrigerant supplied to the heat storage unit 17 via the inlet range EB can flow through the heat storage unit 17, from the inlet range EB to the outlet range AB, and then be discharged from the heat storage unit 17 via the outlet range AB.

[0057] Furthermore, it can be seen that the four branch passages Z1 to Z4 through which the refrigerant flows are assigned to the heat accumulator 17. Branch passages Z1 and Z3 are connected to the inlet range EB, and therefore, here they are fluidically connected (communicated) to the inlet range EB, with branch passage Z1 connected to inlet E1 and branch passage Z3 connected to inlet E2. Branch passages Z2 and Z4 are connected to the outlet range AB, and therefore, here they are fluidly connected (communicated) to the outlet range AB, with branch passage Z2 connected to outlet A1 and branch passage Z4 connected to outlet A2. Thus, the refrigerant flowing through branch passage Z1 can be supplied to inlet E1 via branch passage Z1, and also supplied to the heat accumulator 17 via inlet E1 and introduced into the heat accumulator 17. The refrigerant flowing through branch passage Z3 can be supplied to inlet E2 via branch passage Z3, and also supplied to the heat accumulator 17 via inlet E2 and introduced into the heat accumulator 17. The refrigerant flows through the heat storage unit 17 from inlet E1 to outlet A1, then is led out of the heat storage unit 17 via outlet A1 and introduced into branch line Z2. Therefore, the refrigerant introduced into branch line Z2 can be discharged from the heat storage unit 17 via branch line Z2. The refrigerant flows through the heat storage unit 17 from inlet E2 to outlet A2, then is led out of the heat storage unit 17 via outlet A2 and introduced into branch line Z4. Therefore, the refrigerant introduced into branch line Z4 can be discharged from the heat storage unit 17 via branch line Z4.

[0058] The temperature control device 1 also includes a valve device 27, which in this case comprises at least two or exactly two valves, namely a first valve 28 and a second valve 29. In the embodiments shown in each figure, each valve 28, 29 is formed as a 3-port 2-position switching valve.

[0059] The valve device 27 is switchable between a first switching state shown in Figure 3 and a second switching state shown in Figure 4. In the first switching state, the accumulator 17 is connected to the refrigerant circuit 7 using the valve device 27 so that in the first switching state, the accumulator 17 is fluidly connected to the refrigerant circuit 7 at a first connection point V1 located downstream of the refrigerant compressor 11, upstream of the condenser train 12 and upstream of the bypass train 16, and at a second connection point V2 located upstream of the refrigerant compressor 11, and at least a portion of the refrigerant compressed by the refrigerant compressor 11, particularly the compressor train 9, and can be supplied to the accumulator 17 from the first connection point V1 via the inlet range EB, and the refrigerant discharged from the accumulator 17 via the outlet range AB can be introduced into the refrigerant circuit 7 at the second connection point V2. The second connection point V2 is located downstream of the first expansion valve 15, and further downstream of the second expansion valve 18. In principle, it is conceivable that connection point V2 coincides with the mixing point M. However, in the embodiment shown in Figure 1, connection point V2 is located downstream of the mixing point M. In the first switching state, the refrigerant compressed by the refrigerant compressor 11, particularly at least a portion of the compressor flow, can be supplied from the first connection point V1 to the accumulator 17 via the inlet range EB, particularly inlet E1. In the first switching state, the refrigerant discharged from the accumulator 17 via the outlet range AB, particularly outlet A1, can be introduced into the refrigerant circuit 7 at the second connection point V2. At least in the first switching state, inlet E1 is fluidically connected to the refrigerant circuit 7 at connection point V1, and outlet A1 is fluidically connected to the refrigerant circuit 7 at connection point V2, while inlet E2 and outlet A2 are fluidically separated from the refrigerant circuit 7, particularly using the valve device 27.

[0060] In the second switching state, the accumulator 17 is connected to the refrigerant circuit 7 using a valve device 27 so that the accumulator 17 is fluidly connected to the refrigerant circuit 7 at a first third connection point V3 located upstream of the refrigerant compressor 11 in the second switching state and downstream of the first expansion valve 15 and downstream of the second expansion valve 18 in the refrigerant circuit 7, and at a fourth connection point V4 located downstream of the third connection point V3 and upstream of the refrigerant compressor 11 in the refrigerant circuit 7, particularly in the compressor train 9. As a result, in the second switching state, at least a portion of the total mass flow rate, particularly all of the total mass flow rate, can be supplied to the accumulator 17 from the third connection point V3 via the inlet range EB, and the refrigerant discharged from the accumulator 17 via the outlet range AB, particularly outlet A2, can be introduced into the refrigerant circuit 7, particularly in the compressor train 9, at the fourth connection point V4.

[0061] Basically, it is conceivable that the third connection point V3 coincides with the second connection point V2 and / or the mixing point M. However, here, the third connection point V3 is located downstream of the mixing point M and, in particular, upstream of the second connection point V2. It is also conceivable that the connection point V3 is located upstream of the mixing point M and downstream of the expansion valve 18 in the bypass train 16, or that the connection point V3 is located downstream of the expansion valve 15 and upstream of the mixing point M in the condenser train 12.

[0062] For example, in the first switching state, a third partial mass flow rate of refrigerant can be supplied from connection point V1 to the heat storage unit 17 via inlet E1. At connection point V2, the third partial mass flow rate is introduced into the refrigerant circuit 7, where it is mixed with the total mass flow rate, so that the compressor flow includes the total mass flow rate and the third partial mass flow rate, and therefore the first partial mass flow rate, the second partial mass flow rate and the third partial mass flow rate, in particular, such that the compressor flow is formed by only the first partial mass flow rate, the second partial mass flow rate and the third partial mass flow rate. Thus, for example, the third partial mass flow rate is another partial mass flow rate as described above.

[0063] In both the first and second switching states, branch line Z1 is connected to connection point V1, branch line Z2 to connection point V2, branch line Z3 to connection point V3, and branch line Z4 to connection point V4, all connected to the refrigerant circuit 7. In the first switching state, inlet E1 is fluidically connected to the refrigerant circuit 7 at connection point V1 via branch line Z1, and in the first switching state, outlet A1 is fluidically connected to the refrigerant circuit 7 at connection point V2 via branch line Z2. In the first switching state, the branch line Z3 and its inlet E2 are fluidly separated from the refrigerant circuit 7 using the valve device 27, particularly valve 28. In the first switching state, the branch line Z4 and its outlet A2 are fluidly separated from the refrigerant circuit 7 using the valve device 27, particularly valve 29. Therefore, in the first switching state, the refrigerant from the refrigerant circuit 7 does not flow from connection point V3 through the heat storage unit 17 to connection point V4, or vice versa.

[0064] In the second switching state, the inlet E2 is fluidly connected to the refrigerant circuit 7 at connection point V3 via the branching path Z3 and, in this case, the valve device 27, and especially via valve 28. In the second switching state, the outlet A2 is fluidly connected to the refrigerant circuit 7 at connection point V4 via the branching path Z4 and, in this case, the valve device 27, and especially via valve 29. In the second switching state, the branching path Z2 and thereby the outlet A1 are fluidly separated from the refrigerant circuit 7 using the valve device 27, and especially valve 28. Therefore, in the second switching state, the refrigerant from the refrigerant circuit 7 does not flow from connection point V1 through the heat storage unit 17 to connection point V2, or vice versa.

[0065] Figure 2 shows a phase diagram of a refrigerant formed as, for example, R1234yf. The phase diagram shown in Figure 2 represents the operation of the temperature control device 1 without a heat storage device 17. As is typical, the horizontal axis 20 of the phase diagram is plotted or indicated on the refrigerant, particularly the specific enthalpy, in kilojoules per kilogram. As is typical, the vertical axis 21 of the phase diagram is plotted or indicated on the refrigerant, particularly in bar, and for example, on a logarithmic scale. The saturated vapor line of the refrigerant in the phase diagram is indicated by the symbol 22. Points 1 to 5 are plotted on the phase diagram, so it is possible to observe the enthalpy of the refrigerant at points 1 to 5 from the phase diagram shown in Figure 2. In particular, it can be seen that the enthalpy of the refrigerant is the same at points 1, 4, and 5, and that the enthalpy of the refrigerant is the same at points 2 and 3. In Figure 2, arrow 23 represents the change in the state of the refrigerant from point 1 to point 2, and arrow 24 represents the change in the state of the refrigerant from point 2 to point 5. Arrow 25 represents the change in the state of the refrigerant from point 2 to point 3, and arrow 26 represents the change in the state of the refrigerant from point 3 to point 4. Each change in state can be understood as a change in the thermodynamic state of the refrigerant. It can be seen that a first thermodynamic cycle process, formed as a first triangular process, proceeds through points 1-4, and therefore through the compressor train 9 and condenser train 12, and a second thermodynamic cycle process, formed as a second triangular process, proceeds through points 1, 2, and 5, and therefore through the compressor train and bypass train 16. The triangular processes, also simply called processes, are parallel, and none of the triangular processes are essentially closed. Point 1 is preferably stably located to the right of the saturated vapor line 22 with respect to the phase diagram shown in Figure 2.In other words, it is desirable that the first partial mass flow rate, the second partial mass flow rate, and especially the third partial mass flow rate in the first switching state, and thus the mixing ratio, or especially in the first switching state, the mixing ratio in which the first partial mass flow rate and the second partial mass flow rate or the total mass flow rate and the third partial mass flow rate are mixed with each other, be adjusted using expansion valves 15, 18, and also, for example, a third expansion valve 30, so that, with respect to the phase diagram shown in Figure 2, the enthalpy of the refrigerant at point 1, or within point 1, is reliably or stably located to the right of the saturated vapor line 22. The above-mentioned and later configurations for expansion valves 15, 18 are also readily applicable to expansion valve 30. It can be seen that the temperature control device 1 is equipped with a third expansion valve 30, which is located downstream of the first connection point V1 and upstream of the second connection point V2 in the first switching state, and at the same time downstream of the heat accumulator 17 and upstream of the second connection point V2. In the first switching state, the third partial mass flow rate passing through the heat accumulator 17 is adjusted, or adjusted, i.e., changed, or changed, and consequently altered, or altered using the third expansion valve 30. For example, the third expansion valve 30 has a third flow cross-section through which the third partial mass flow rate can pass, and this third flow cross-section is adjustable, i.e., alterable or changeable by controlling the expansion valve 30, which is controllable (operable) using the electronic computing unit 19, depending in particular on a specific pressure and a specific temperature. For this purpose, for example, the third expansion valve 30 includes a third actuator, which is particularly electrically operable, and the third flow cross-section can be adjusted, i.e., altered by controlling the expansion valve 30 using this third actuator.By adjusting the first, second, and third partial mass flow rates, the total mass flow rate, which consists of the first, second, and third partial mass flow rates, can be adjusted, particularly in the first switching state, by introducing the third partial mass flow rate at connection point V2 into the refrigerant circuit 7 and thus the total mass flow rate, i.e., into the first and second partial mass flow rates, and mixing it with the first and second partial mass flow rates or the total mass flow rate. Therefore, it is desirable that the first, second, and third partial mass flow rates, and thus the mixing ratio, and preferably the overall mixing ratio, also called the overall mixing ratio, be adjusted using the expansion valves 15, 18, and 30 so that the enthalpy of the refrigerant is reliably or stably located at point 1 with respect to the phase diagram shown in Figure 2, or within point 1, to the right of the saturated vapor line 22. This makes it possible to ensure that the compressor flow is at least mainly superheated steam, and especially superheated steam only. In other words, this prevents wet vapor or liquid from passing through the refrigerant compressor 11, which could lead to damage to the refrigerant compressor 11. Such operation of the temperature control device 6, in relation to the phase diagram shown in Figure 2, where the enthalpy of the refrigerant is reliably located to the right of the saturated vapor line 22 at point 1 or within point 1, is also called stable stabilization.

[0066] Figure 2 shows that the refrigerant has a first enthalpy at or within the first point 1, a second enthalpy at or within the second point, a third enthalpy at or within the third point, a fourth enthalpy at or within the fourth point, and a fifth enthalpy at or within the fifth point. 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, particularly the same first pressure, at or within points 1, 4, and 5. In Figure 2, the sixth point 31 represents the enthalpy of the refrigerant located on the saturated vapor line 22 of the refrigerant, which belongs to the first pressure. The enthalpy of the refrigerant, represented by point 31, which belongs to the first pressure and lies on the saturated vapor line 22 of the refrigerant, is also called the saturated vapor line enthalpy.

[0067] By using the heat accumulator 17, and by the fact that the heat accumulator 17 can selectively receive heat from the refrigerant, particularly in a first switching state, or release heat stored in the heat accumulator 17 to the refrigerant, particularly in a second switching state, it is possible to influence the temperature and enthalpy of the refrigerant in a particularly required and advantageous manner, and in particular to change the temperature and enthalpy of the refrigerant, without having to operate the refrigerant compressor 11 in an excessively different manner. In other words, the refrigerant compressor 11 can be operated in a particularly efficient operating point, particularly in the same efficient operating point, so that the liquefaction unit can be operated or provided with different powers.

[0068] Figure 1 shows that the temperature control device 6 is equipped with, for example, a check valve 32. In the first switching state, the check valve is arranged in series with respect to the expansion valve 30 and the heat accumulator 17, such that the check valve 32 is located 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 configured to automatically close in the direction of the heat accumulator 17, and therefore to automatically prevent the flow of refrigerant from the connection point V2 through the check valve 32 to the heat accumulator 17. In addition, the check valve 32 is configured to automatically open in the direction of the connection point V2, and therefore to automatically allow the flow of refrigerant from the heat accumulator 17 through the check valve 32 to the connection point V2. This makes it possible to prevent accidental backflow of refrigerant from the connection point V2 to the heat accumulator 17. Preferably, the refrigerant compressor 11 is an electric refrigerant compressor, also known as an eKMV. [Explanation of symbols]

[0069] 1 point 2 points 3 points 4 points 5 points 6 Temperature control device 7 Refrigerant Circuit 9 Compressor Train 11 Refrigerant compressor 12 Condenser train 14 Condenser 15 First expansion valve 16 Bypass Train 17 Heat storage 18. Second expansion valve 19 Electronic computing device 20 Horizontal axis 21 Vertical axis 22 Saturated vapor lines 23 Arrows 24 Arrows 25 Arrows 26 Arrows 27 Valve device 28 valves 29 valves 30 Expansion valve 31 points 32 Check valve AB Exit Range A1 exit A2 exit D1 Enthalpy Difference D2 Enthalpy Difference EB entry range E1 entrance E2 entrance A branching point M Mixing point V1 First connection point V2 Second connection point V3 Third connection point V4 4th Connection User S1 Sensor device S2 Sensor Device S3 Sensor Device Z1 Junction Z2 Junction Z3 Junction Z4 Intersection

Claims

1. A temperature control device (6) for controlling the temperature of at least one partial range of a motorized vehicle, - A refrigerant circuit (7) through which the refrigerant flows, - A compressor train (9) through which refrigerant can flow, on which a refrigerant compressor (11) capable of transporting and compressing refrigerant is located. - A condenser train (12) through which the first partial mass flow rate (13) of the refrigerant can flow, which is connected in series with the compressor train (9) and thereby has a first expansion valve (15) that can adjust and expand the first partial mass flow rate (13) and a condenser (14) that can condense the first partial mass flow rate (13). - A bypass train (16) connected in parallel to the condenser train (12) and in series to the compressor train (9), thereby allowing a second partial mass flow rate (17) of the refrigerant to pass through, and having a second expansion valve (18) that can adjust and expand the second partial mass flow rate (17), and - The condensing train (12) and the bypass train (16) merge, and the first partial mass flow rate (13) and the second partial mass flow rate (17) merge into the total mass flow rate, thereby mixing them together at the mixing point (M). The refrigerant circuit (7) is provided with, - A heat storage device (17) formed to store heat, - The inlet range (EB) is capable of supplying refrigerant to the heat storage unit (17) such that heat can be selectively stored in the heat storage unit (17) from the refrigerant supplied to the heat storage unit (17) via the inlet range (EB), or heat can be transferred from the heat storage unit (17) to the refrigerant supplied to the heat storage unit (17) via the inlet range (EB), and - An outlet range (AB) from which the refrigerant supplied to the heat storage unit (17) via the inlet range (EB) can be discharged from the heat storage unit (17). The heat storage device (17) is equipped with, - Valve device (27), wherein the valve device is - The first switching state is such that the heat regenerator (17) is fluidly connected to the refrigerant circuit (7) at a first connection point (V1) located downstream of the refrigerant compressor (11) in the refrigerant circuit (7), upstream of the condenser train (12) and upstream of the bypass train (16), and at a second connection point (V) located upstream of the refrigerant compressor (11) in the refrigerant circuit (7) and downstream of the first expansion valve (15) and / or the second expansion valve (18), thereby enabling at least a portion of the refrigerant compressed using the refrigerant compressor (11) to be supplied to the heat regenerator (17) from the first connection point (V1) through the inlet range (EB), and enabling the refrigerant discharged from the heat regenerator (17) through the outlet range (AB) to be introduced into the refrigerant circuit (7) at the second connection point (V2), - The heat accumulator (17) is located upstream of the refrigerant compressor (11) in the refrigerant circuit (7), and is fluidly connected to the refrigerant circuit (7) at a third connection point (V) located downstream of the first expansion valve (15) and / or downstream of the second expansion valve (18) in the refrigerant circuit (7), and at a fourth connection point (V4) located downstream of the third connection point (V3) and upstream of the refrigerant compressor (11) in the refrigerant circuit (7), thereby enabling at least a portion of the total mass flow rate to be supplied to the heat accumulator (17) from the third connection point (V3) through the inlet range (EB), and enabling the refrigerant discharged from the heat accumulator (17) through the outlet range (AB) to be introduced into the refrigerant circuit (7) at the fourth connection point (V4), in a second switching state. The valve device (27) is switchable between and A temperature control device (6) characterized by having the following features.

2. The temperature control device (6) according to claim 1, characterized in that the heat storage device (17) is formed as a latent heat storage device having at least one phase change material for storing heat.

3. The temperature control device (6) according to claim 2, characterized in that the phase change material has a melting temperature in the range of 50 degrees Celsius or more and 90 degrees Celsius or less.

4. The temperature control device (6) according to claim 3, characterized in that the melting temperature is in the range of 75 degrees Celsius or more and 90 degrees Celsius or less.

5. The temperature control device (6) according to claim 4, characterized in that the melting temperature is in the range of 75 degrees Celsius or more and 80 degrees Celsius or less.

6. The temperature control device (6) according to claim 3, characterized in that the melting temperature is in the range of 50 degrees Celsius or more and 80 degrees Celsius or less.

7. The temperature control device (6) according to any one of claims 1 to 6, characterized in that, in the first switching state, a third expansion valve (30) capable of adjusting and expanding the third partial mass flow rate of refrigerant supplied to the heat accumulator (17) via the inlet range (17) in the first switching state is connected in series with the heat accumulator (17) such that, in the first switching state, the third expansion valve (30) is located downstream of the first connection point (V1) and upstream of the second connection point (V2).

8. The temperature control device (6) according to claim 7, characterized in that, in the first switching state, the third expansion valve (30) is connected in series with the heat accumulator (17) such that the third expansion valve (30) is located downstream of the heat accumulator (17) and upstream of the second connection point (V2) in the first switching state.

9. A method for operating the temperature control device (6) according to any one of claims 1 to 8.

10. A motorized vehicle having at least one temperature control device (6) according to any one of claims 1 to 8.

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